EP3128259A1 - Heat pump device - Google Patents
Heat pump device Download PDFInfo
- Publication number
- EP3128259A1 EP3128259A1 EP14886307.9A EP14886307A EP3128259A1 EP 3128259 A1 EP3128259 A1 EP 3128259A1 EP 14886307 A EP14886307 A EP 14886307A EP 3128259 A1 EP3128259 A1 EP 3128259A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- pipe
- liquid pipe
- gas pipe
- outdoor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Images
Classifications
-
- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
- C09K5/02—Materials undergoing a change of physical state when used
- C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
- C09K5/041—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems
- C09K5/044—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds
- C09K5/045—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds containing only fluorine as halogen
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
- C10M171/00—Lubricating compositions characterised by purely physical criteria, e.g. containing as base-material, thickener or additive, ingredients which are characterised exclusively by their numerically specified physical properties, i.e. containing ingredients which are physically well-defined but for which the chemical nature is either unspecified or only very vaguely indicated
- C10M171/008—Lubricant compositions compatible with refrigerants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
-
- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
- C09K2205/10—Components
- C09K2205/12—Hydrocarbons
- C09K2205/126—Unsaturated fluorinated hydrocarbons
-
- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
- C09K2205/22—All components of a mixture being fluoro compounds
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
- C10M2207/00—Organic non-macromolecular hydrocarbon compounds containing hydrogen, carbon and oxygen as ingredients in lubricant compositions
- C10M2207/04—Ethers; Acetals; Ortho-esters; Ortho-carbonates
- C10M2207/0406—Ethers; Acetals; Ortho-esters; Ortho-carbonates used as base material
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
- C10M2207/00—Organic non-macromolecular hydrocarbon compounds containing hydrogen, carbon and oxygen as ingredients in lubricant compositions
- C10M2207/10—Carboxylix acids; Neutral salts thereof
- C10M2207/103—Carboxylix acids; Neutral salts thereof used as base material
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
- C10M2207/00—Organic non-macromolecular hydrocarbon compounds containing hydrogen, carbon and oxygen as ingredients in lubricant compositions
- C10M2207/28—Esters
- C10M2207/2805—Esters used as base material
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
- C10M2207/00—Organic non-macromolecular hydrocarbon compounds containing hydrogen, carbon and oxygen as ingredients in lubricant compositions
- C10M2207/28—Esters
- C10M2207/283—Esters of polyhydroxy compounds
- C10M2207/2835—Esters of polyhydroxy compounds used as base material
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
- C10M2207/00—Organic non-macromolecular hydrocarbon compounds containing hydrogen, carbon and oxygen as ingredients in lubricant compositions
- C10M2207/28—Esters
- C10M2207/30—Complex esters, i.e. compounds containing at leasst three esterified carboxyl groups and derived from the combination of at least three different types of the following five types of compounds: monohydroxyl compounds, polyhydroxy xompounds, monocarboxylic acids, polycarboxylic acids or hydroxy carboxylic acids
- C10M2207/301—Complex esters, i.e. compounds containing at leasst three esterified carboxyl groups and derived from the combination of at least three different types of the following five types of compounds: monohydroxyl compounds, polyhydroxy xompounds, monocarboxylic acids, polycarboxylic acids or hydroxy carboxylic acids used as base material
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
- C10M2209/00—Organic macromolecular compounds containing oxygen as ingredients in lubricant compositions
- C10M2209/02—Macromolecular compounds obtained by reactions only involving carbon-to-carbon unsaturated bonds
- C10M2209/04—Macromolecular compounds obtained by reactions only involving carbon-to-carbon unsaturated bonds containing monomers having an unsaturated radical bound to an alcohol or ester thereof; bound to an aldehyde, ketonic, ether, ketal or acetal radical
- C10M2209/043—Macromolecular compounds obtained by reactions only involving carbon-to-carbon unsaturated bonds containing monomers having an unsaturated radical bound to an alcohol or ester thereof; bound to an aldehyde, ketonic, ether, ketal or acetal radical used as base material
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
- C10M2209/00—Organic macromolecular compounds containing oxygen as ingredients in lubricant compositions
- C10M2209/10—Macromolecular compoundss obtained otherwise than by reactions only involving carbon-to-carbon unsaturated bonds
- C10M2209/103—Polyethers, i.e. containing di- or higher polyoxyalkylene groups
- C10M2209/1033—Polyethers, i.e. containing di- or higher polyoxyalkylene groups used as base material
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
- C10N2020/00—Specified physical or chemical properties or characteristics, i.e. function, of component of lubricating compositions
- C10N2020/09—Characteristics associated with water
- C10N2020/097—Refrigerants
- C10N2020/101—Containing Hydrofluorocarbons
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
- C10N2030/00—Specified physical or chemical properties which is improved by the additive characterising the lubricating composition, e.g. multifunctional additives
- C10N2030/10—Inhibition of oxidation, e.g. anti-oxidants
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
- C10N2030/00—Specified physical or chemical properties which is improved by the additive characterising the lubricating composition, e.g. multifunctional additives
- C10N2030/70—Soluble oils
-
- C—CHEMISTRY; METALLURGY
- C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
- C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
- C10N2040/00—Specified use or application for which the lubricating composition is intended
- C10N2040/30—Refrigerators lubricants or compressors lubricants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
- F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/12—Inflammable refrigerants
- F25B2400/121—Inflammable refrigerants using R1234
Definitions
- the present invention relates to an air-conditioning apparatus to which a refrigerant having lower global warming potential (GWP) than R410A is applied.
- GWP global warming potential
- Known air-conditioning apparatus utilize heat pump cycles with HFC refrigerant R410A.
- refrigerants having lower global warming potential than R410A are being developed.
- Refrigerants with lower GWP than R410A may be HFC32 (difluoromethane), HFO-1234yf (2,3,3,3-tetrafluoropropane), and HFO-1123 (1,1,2-trifluoroethylene).
- HFO hydrofluoroolefin
- HFC hydrofluorocarbon
- HFO-1123 (GWP100: 0.3) has lower GWP than HFC32 (GWP100: 675) and HFO-1234yf (GWP100: 4).
- HFO-1123 has lower GWP than HFC32 (GWP100: 675) and HFO-1234yf (GWP100: 4).
- Patent Literature 1 International Publication No. WO 2012/157764 A1
- a decomposition reaction of HFO-1123 may induce a subsequent series of decomposition reactions.
- the outer diameter of the refrigerant pipe must be increased to reduce the pressure in the refrigerant pipe.
- an increased outer diameter of refrigerant pipes results in increased costs of the refrigerant pipes.
- the present invention provides a heat pump apparatus including:
- the present invention provides heat pump apparatus including
- the present invention provides a heat pump apparatus including:
- the present invention provides a heat pump apparatus including:
- the present invention can provide an inexpensive air-conditioning apparatus that utilizes HFO-1123 by using gas pipes and liquid pipes depending on the cooling capacity of an outdoor unit.
- hydrofluorocarbon (HFC) refrigerants are hydrocarbons having fluorine (F) and no chlorine (CI) in their molecular structures.
- Hydrofluoroolefin (HFO) refrigerants are hydrocarbons having fluorine and no chlorine in their molecular structures and further have a carbon-carbon double bond. HFO refrigerants are included in HFC refrigerants.
- Fig. 1 illustrates a refrigerant circuit of a heat pump apparatus 100 according to Embodiment 1.
- the refrigerant circuit of the heat pump apparatus 100 will be described below with reference to Fig. 1 .
- the heat pump apparatus 100 is an air-conditioning apparatus that can be switched between cooling operation and heating operation.
- the heat pump apparatus 100 includes an outdoor unit 10 and an indoor unit 20.
- the outdoor unit 10 is placed outdoors, and the indoor unit 20 is placed in a room to be air-conditioned.
- the outdoor unit 10 includes an accumulator 11, a compressor 12, a four-way valve 13, an outdoor heat exchanger 14, a gas pipe joint 16, and a liquid pipe joint 17.
- the indoor unit 20 includes an indoor heat exchanger 21, a gas pipe joint 22, and a liquid pipe joint 23.
- the outdoor unit 10 and the indoor unit 20 are connected through the gas pipe 30 and the liquid pipe 40.
- the gas pipe 30 is coupled to the gas pipe joint 16 and the gas pipe joint 22.
- the liquid pipe 40 is connected to the liquid pipe joint 17 and the liquid pipe joint 23.
- the accumulator 11 contains liquid refrigerant and gas refrigerant.
- the gas refrigerant is sucked into the compressor 12.
- High-temperature low-pressure gas refrigerant sucked into the compressor 12 is compressed and is discharged as a high-temperature high-pressure gas refrigerant.
- the refrigerant flow path can be changed with the four-way valve 13 to switch between a flow path for cooling operation and a flow path for heating operation.
- the heat pump apparatus 100 according to Embodiment 1 includes the accumulator 11, the accumulator 11 is not necessarily required.
- a high-temperature high-pressure gas refrigerant discharged from the compressor 12 flows into the four-way valve 13.
- the high-temperature high-pressure gas refrigerant flows through the four-way valve 13, the gas pipe joint 16, the gas pipe 30, and the gas pipe joint 22 into the indoor heat exchanger 21.
- the high-temperature high-pressure gas refrigerant exchanges heat with indoor air in the indoor heat exchanger 21 and becomes a low-temperature high-pressure liquid refrigerant.
- the low-temperature high-pressure liquid refrigerant from the indoor heat exchanger 21 flows through the liquid pipe joint 23, the liquid pipe 40, and the liquid pipe joint 17 into an expansion valve 15.
- the low-temperature high-pressure liquid refrigerant is depressurized by the expansion valve 15 and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant.
- the low-temperature low-pressure two-phase gas-liquid refrigerant from the expansion valve 15 flows into the outdoor heat exchanger 14.
- the low-temperature low-pressure two-phase gas-liquid refrigerant exchanges heat with outdoor air in the outdoor heat exchanger 14 and becomes a high-temperature low-pressure gas refrigerant.
- the high-temperature low-pressure gas refrigerant from the outdoor heat exchanger 14 flows through the four-way valve 13 into the accumulator 11.
- the high-temperature high-pressure gas refrigerant exchanges heat with outdoor air in the outdoor heat exchanger 14 and becomes a low-temperature high-pressure liquid refrigerant.
- the low-temperature high-pressure liquid refrigerant from the outdoor heat exchanger 14 flows into the expansion valve 15.
- the low-temperature high-pressure liquid refrigerant is depressurized by the expansion valve 15 and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant.
- the low-temperature low-pressure two-phase gas-liquid refrigerant from the expansion valve 15 flows through the liquid pipe joint 17, the liquid pipe 40, and the liquid pipe joint 23 into the indoor heat exchanger 21.
- the low-temperature low-pressure two-phase gas-liquid refrigerant exchanges heat with indoor air in the indoor heat exchanger 21 and becomes a high-temperature low-pressure gas refrigerant.
- the high-temperature low-pressure gas refrigerant from the indoor heat exchanger 21 flows through the gas pipe joint 22, the gas pipe 30, the gas pipe joint 16, and the four-way valve 13 into the accumulator 11.
- a high-temperature high-pressure gas refrigerant flows through the gas pipe 30, and in cooling operation, a high-temperature low-pressure gas refrigerant flows through the gas pipe 30.
- a refrigerant used in the present invention (Embodiments 1 to 3) will be described below.
- a refrigerant circulating through the heat pump apparatus is HFO-1123.
- HFO-1123 has a GWP100 of 0.4, which is much lower than those of R410A and HFC32, and is preferred in terms of global warming mitigation. When HFO-1123 is applied to heat pump apparatus, however, HFO-1123 may cause a decomposition reaction, and problems resulting from the decomposition reaction must be solved.
- Fig. 2 shows a decomposition reaction formula of HFO-1123.
- the decomposition reaction is a disproportionation reaction in which 1 mol of HFO-1123 yields 1/2 mol of carbon tetrafluoride (CF 4 ), 2/3 mol of carbon (C), and 1 mol of hydrogen fluoride (HF).
- the decomposition reaction is also an exothermic reaction in which 1 mol of HFO-1123 generates approximately 45 kcal of heat.
- HFO-1123 Use of high-purity HFO-1123 may cause a series of decomposition reactions once HFO-1123 decomposes. Thus, a decomposition reaction of HFO-1123 may increase refrigerant pressure beyond expectations in a refrigerant pipe. Furthermore, HFO-1123 is slightly flammable, and leakage of high-temperature HFO-1123 from a pipe may cause a fire.
- a decomposition reaction of HFO-1123 yields hydrogen fluoride (HF).
- Hydrogen fluoride dissolved in water produces acidic hydrofluoric acid.
- Hydrofluoric acid may corrode an inner surface of a refrigerant pipe.
- the acidity of hydrofluoric acid increases with decreasing temperature.
- the liquid pipe 40 through which a low temperature refrigerant flows may be corroded.
- a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123 is used to prevent pressure increase in refrigerant pipes and corrosion of pipes.
- the addition of an HFC refrigerant (other than HFO-1123) to HFO-1123 can suppress the decomposition reaction of HFO-1123 compared with the addition of a natural refrigerant, such as carbon dioxide or propane.
- HFO-1234yf or HFC32 can further suppress a series of decomposition reactions of HFO-1123 compared with the addition of other HFC refrigerants and HFO refrigerants. It is desirable to add HFC32 rather than HFO-1234yf in view of the energy efficiency of heat pump apparatus.
- a particular refrigerant is mixed with HFO-1123 to prevent the decomposition reaction of HFO-1123, and pipes having an outer diameter optimum for the mixed refrigerant are selected.
- the outer diameter of selected pipes will be described later.
- refrigerating machine oil is mixed with refrigerant as lubricating oil for lubricating slide portions of compressors.
- refrigerant as lubricating oil for lubricating slide portions of compressors.
- ether lubricating oils and ester lubricating oils are hygroscopic and are likely to produce sludge due to hydrolysis, and are therefore sometimes difficult to use in heat pump apparatus in consideration of the reliability of compressors.
- hydrolysis of ether lubricating oils and ester lubricating oils can remove water from pipes and thereby reduce the proportion of hydrogen fluoride that dissolves in water and produces hydrofluoric acid. This can suppress corrosion of pipes caused by hydrogen fluoride.
- the design pressure P refers to a pressure that depends on the type of refrigerant, the amount of refrigerant, and the maximum pressure in refrigerant circuit operation, and provides a standard for the pressure resistance of the product.
- the efficiency ⁇ of welded joints is a dimensionless number specified in Japanese Industrial Standards "JIS B 8265 Construction of pressure vessel".
- JIS B 8265 Construction of pressure vessel For example, welded joints in the form of "one side full thickness fillet welded lap joint without plug welding" have an efficiency ⁇ of 0.45.
- the outer diameter ⁇ of pipes must be larger in the case of HFO-1123 than in the case of R410A, which does not cause a series of decomposition reactions.
- the required thickness t of pipes must be greater in the case of HFO-1123 than in the case of R410A.
- the design pressure P or the efficiency ⁇ of welded joints may be increased to prevent the outer diameter ⁇ and the required thickness t of pipes from being increased.
- a higher design pressure P results in an increased cost of a design change to improve the safety of the compressor 12.
- increased labor costs are necessary, due to a lot of time and effort to perform welding. It may be impossible to increase the efficiency ⁇ of welded joints in some welding methods.
- Fig. 3 is a table showing the relationship between cooling capacity and the types of gas pipe and liquid pipe of the heat pump apparatus 100.
- the cooling capacity refers to the heat exchange capacity (kW) of the outdoor unit 10 in cooling operation measured under the following conditions (temperature conditions for mild climatic zone) specified in Japanese Industrial Standards "JIS B 8615-1 ".
- Fig. 3 shows the outer diameters ⁇ (mm) of the gas pipe 30 and the liquid pipe 40 usable depending on the cooling capacity of the outdoor unit 10 according to Embodiment 1.
- the cooling capacity of the outdoor unit 10 depends on the performance of the compressor 12, the size of the outdoor heat exchanger 14, the amount of refrigerant to be supplied, and other parameters.
- the design pressure of the heat pump apparatus 100 depends on the cooling capacity of the outdoor unit 10.
- the possible outer diameters of the gas pipe 30 and the liquid pipe 40 are determined on the basis of the mathematical formula (1). It is desirable that the percentage of HFC32 to be mixed be 20% or more by weight and 60% or less by weight.
- the percentage of HFC32 to be mixed in Embodiments 2 and 3 is the same as in Embodiment 1.
- ⁇ 15.9 refers to ⁇ 15.88.
- Pipes to be used are made of phosphorus deoxidized copper.
- a pipe to be used as the gas pipe 30 most desirably has an outer diameter ⁇ of 9.52 mm ( ⁇ is hereinafter omitted) (corresponding to "double circle”), more desirably 6.35 mm (corresponding to "circle”), desirably 12.7 mm (corresponding to "triangle”).
- a pipe having an outer diameter of 15.9 mm or more cannot be used.
- a pipe to be used as the liquid pipe 40 most desirably has an outer diameter of 6.35 mm (corresponding to "double circle"), more desirably 9.52 mm (corresponding to "circle”), desirably 12.7 mm (corresponding to "triangle”).
- the outdoor unit 10 having a cooling capacity of 2.5 kW has the same results as the outdoor unit 10 having a cooling capacity of 2.2 kW.
- a pipe to be used as the gas pipe 30 most desirably has an outer diameter of 9.52 mm (corresponding to “double circle”), second most desirably 6.35 or 12.7 mm (corresponding to "circle”), third most desirably 15.9 mm (corresponding to "triangle").
- the liquid pipe 40 has the same results as in the case of a cooling capacity of 2.2 or 2.5 kW.
- a pipe to be used as the gas pipe 30 most desirably has an outer diameter of 12.7 mm (corresponding to “double circle”), second most desirably 9.52 or 15.9 mm (corresponding to "circle”), third most desirably 6.53 mm (corresponding to "triangle").
- the liquid pipe 40 has the same results as in the case of a cooling capacity of 2.2 or 2.5 kW.
- a pipe to be used as the gas pipe 30 most desirably has an outer diameter of 12.7 mm (corresponding to “double circle”), second most desirably 9.52 or 15.9 mm (corresponding to "circle”).
- the liquid pipe 40 most desirably has an outer diameter of 9.52 mm (corresponding to "double circle”), second most desirably 6.35 or 12.7 mm (corresponding to "circle”).
- Fig. 4 shows the ratios (mm/kW) of the outer diameters of the gas pipe 30 and the liquid pipe 40 to cooling capacity.
- the ratio (mm/kW) of the outer diameter of the gas pipe 30 to cooling capacity desirably ranges from 1.00 to 5.77 (corresponding to “double circle”, “circle”, or “triangle"), more desirably 1.00 to 4.54 (corresponding to “double circle” or “circle”), most desirably 1.34 to 4.33 (corresponding to "double circle”).
- the outer diameter of the gas pipe 30 is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of the outdoor unit 10 ranges from 0.67 to 5.77.
- the ratio (mm/kW) of the outer diameter of the liquid pipe 40 to cooling capacity desirably ranges from 0.67 to 5.77 (corresponding to “double circle”, “circle”, or “triangle"), more desirably 0.67 to 4.33 (corresponding to “double circle” or “circle”), most desirably 1.00 to 2.89 (corresponding to "double circle”).
- the outer diameter of the liquid pipe 40 is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of the outdoor unit 10 ranges from 1.00 to 5.77.
- an HFC refrigerant particularly HFO-1234yf in the case of HFO refrigerants or HFC32 in the case of HFC refrigerants, is mixed to suppress the decomposition reaction of HFO-1123.
- the optimum outer diameters of pipes to be used as the gas pipe 30 and the liquid pipe 40 can be chosen on the assumption that the decomposition reaction of HFO-1123 is suppressed, and this can reduce the cost of the heat pump apparatus 100.
- a heat pump apparatus 200 described in Embodiment 2 includes a plurality of indoor units coupled to one outdoor unit.
- the heat pump apparatus 200 includes three indoor units 20A, 20B, and 20C coupled to one outdoor unit 10A.
- the outdoor unit 10A includes no expansion valve, and the indoor units 20A, 20B, and 20C include expansion valves 24a, 24b, and 24c, respectively.
- the gas pipes of the heat pump apparatus 200 are composed of a main gas pipe 30a, a gas pipe 31, a gas pipe 32a, a gas pipe 32b, and a gas pipe 32c.
- the liquid pipes of the heat pump apparatus 200 are composed of a main liquid pipe 40a, a liquid pipe 41, a liquid pipe 42a, a liquid pipe 42b, and a liquid pipe 42c.
- the main gas pipe 30a, the gas pipe 31, the gas pipe 32a, the gas pipe 32b, and the gas pipe 32c are coupled together with a branch joint 50a and a branch joint 50b.
- the main liquid pipe 40a, the liquid pipe 41, the liquid pipe 42a, the liquid pipe 42b, and the liquid pipe 42c are coupled together with a branch joint 55a and a branch joint 55b.
- the branch joint 50a, the branch joint 50b, the branch joint 55a, and the branch joint 55b are three-way branch joints each having opening ports in three directions.
- the three opening ports of the branch joint 50a are coupled to the main gas pipe 30a, the gas pipe 31, and the gas pipe 32a.
- the three opening ports of the branch joint 50b are coupled to the gas pipe 31, the gas pipe 32c, and the gas pipe 32b.
- the three opening ports of the branch joint 55a are coupled to the main liquid pipe 40a, the liquid pipe 41, and the liquid pipe 42a.
- the three opening ports of the branch joint 55b are coupled to the liquid pipe 41, the liquid pipe 42c, and the liquid pipe 42b.
- the gas pipe 32a is coupled to a gas pipe joint 22a of the indoor unit 20A
- the gas pipe 32b is coupled to the gas pipe joint 22b of the indoor unit 20B
- the gas pipe 32c is coupled to the gas pipe joint 22c of the indoor unit 20C.
- the liquid pipe 42a is coupled to the liquid pipe joint 23a of the indoor unit 20A
- the liquid pipe 42b is coupled to the liquid pipe joint 23b of the indoor unit 20B
- the liquid pipe 42c is coupled to the liquid pipe joint 23c of the indoor unit 20C.
- a high-temperature high-pressure gas refrigerant discharged from a compressor 12a flows into a four-way valve 13a.
- the high-temperature high-pressure gas refrigerant flows from the four-way valve 13a to the gas pipe joint 16a, the main gas pipe 30a, and the branch joint 50a.
- the refrigerant is divided by the branch joint 50a into the gas pipe 32a and the gas pipe 31.
- the refrigerant flowing through the gas pipe 31 is divided by the branch joint 50b into the gas pipe 32b and the gas pipe 32c.
- the high-temperature high-pressure gas refrigerant flows through the gas pipes 32a, 32b, and 32c and the gas pipe joint 22a, the gas pipe joint 22b, and the gas pipe joint 22c into indoor heat exchangers 21 a, 21 b, and 21c of the indoor units 20A, 20B, and 20C.
- the high-temperature high-pressure gas refrigerant exchanges heat in the indoor heat exchangers 21 a, 21 b, and 21c and becomes a low-temperature high-pressure liquid refrigerant, and is depressurized by the expansion valves 24a, 24b, and 24c and becomes a low-temperature high-pressure two-phase gas-liquid refrigerant.
- the low-temperature high-pressure two-phase gas-liquid refrigerant from the expansion valve 24a flows through the liquid pipe 42a, the branch joint 55a, the main liquid pipe 40a, and the liquid pipe joint 17a into an outdoor heat exchanger 14a.
- the low-temperature high-pressure two-phase gas-liquid refrigerant from the expansion valve 24b flows through the liquid pipe 42b, the branch joint 55b, the liquid pipe 41, the branch joint 55a, the main liquid pipe 40a, and the liquid pipe joint 17a into the outdoor heat exchanger 14a.
- the low-temperature high-pressure two-phase gas-liquid refrigerant from the expansion valve 24c flows through the liquid pipe 42c, the branch joint 55b, the liquid pipe 41, the branch joint 55a, the main liquid pipe 40a, and the liquid pipe joint 17a into the outdoor heat exchanger 14a.
- the low-temperature high-pressure two-phase gas-liquid refrigerant from the expansion valves 24a, 24b, and 24c exchanges heat with outdoor air in the outdoor heat exchanger 14a and becomes a high-temperature low-pressure gas refrigerant.
- the high-temperature low-pressure gas refrigerant from the outdoor heat exchanger 14a flows through the four-way valve 13a into an accumulator 11 a.
- a high-temperature high-pressure gas refrigerant discharged from the compressor 12a flows through the four-way valve 13a into the outdoor heat exchanger 14a.
- the high-temperature high-pressure gas refrigerant exchanges heat with outdoor air in the outdoor heat exchanger 14a and becomes a low-temperature high-pressure liquid refrigerant.
- the low-temperature high-pressure liquid refrigerant from the outdoor heat exchanger 14a flows through the liquid pipe joint 17a and the main liquid pipe 40a into the branch joint 55a.
- the refrigerant is divided by the branch joint 55a into the liquid pipe 41 and the liquid pipe 42a.
- the refrigerant flowing through the liquid pipe 41 is divided by the branch joint 55b into the liquid pipe 42b and the liquid pipe 42c.
- the low-temperature high-pressure liquid refrigerant flows through the liquid pipe 42a, the liquid pipe 42b, and the liquid pipe 42c and the liquid pipe joint 23a, the liquid pipe joint 23b, and the liquid pipe joint 23c into the expansion valve 24a, the expansion valve 24b, and the expansion valve 24c.
- the low-temperature high-pressure liquid refrigerant are depressurized by the expansion valve 24a, the expansion valve 24b, and the expansion valve 24c and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant.
- the low-temperature low-pressure two-phase gas-liquid refrigerant from the expansion valve 24a, the expansion valve 24b, and the expansion valve 24c flows into the indoor heat exchanger 21 a, the indoor heat exchanger 21 b, and the indoor heat exchanger 21 c, exchanges heat with indoor air, and becomes a high-temperature low-pressure gas refrigerant.
- the high-temperature low-pressure gas refrigerant from the indoor heat exchanger 21 a flows through the gas pipe joint 22a, the gas pipe 32a, the branch joint 50a, and the main gas pipe 30a.
- the high-temperature low-pressure gas refrigerant from the indoor heat exchanger 21 b flows through the gas pipe joint 22b, the gas pipe 32b, the branch joint 50b, the gas pipe 31, the branch joint 50a, and the main gas pipe 30a.
- the high-temperature low-pressure gas refrigerant from the indoor heat exchanger 21 c flows through the gas pipe joint 22c, the gas pipe 32c, the gas pipe 32c, the branch joint 50b, the gas pipe 31, the branch joint 50a, and the main gas pipe 30a.
- the high-temperature low-pressure gas refrigerant flowing through the main gas pipe 30a flows through the gas pipe joint 16a and the four-way valve 13a into the accumulator 11 a.
- a high-temperature high-pressure gas refrigerant flows through the main gas pipe 30a, and in cooling operation, a high-temperature low-pressure gas refrigerant flows through the main gas pipe 30a.
- a low-temperature high-pressure two-phase gas-liquid refrigerant flows through the main liquid pipe 40a, and in cooling operation, low-temperature high-pressure liquid refrigerant flows through the main liquid pipe 40a.
- the outer diameter and thickness of the main gas pipe 30a and the main liquid pipe 40a satisfy the following conditions.
- the amount of refrigerant flowing through the main gas pipe 30a into the gas pipe 31 is decreased by the amount of refrigerant flowing through the branch joints 50a and 55a into the indoor unit 20A.
- the gas pipe 31 can have a smaller outer diameter and thickness than the main gas pipe 30a.
- the amount of refrigerant flowing through the main liquid pipe 40a into the liquid pipe 41 is decreased by the amount of refrigerant flowing into the indoor unit 20A.
- the liquid pipe 41 can have a smaller outer diameter and thickness than the main liquid pipe 40a.
- Fig. 6 shows the outer diameters ⁇ (mm) of the main gas pipe 30a and the main liquid pipe 40a usable depending on the cooling capacity of the outdoor unit 10A according to Embodiment 2.
- Fig. 7 shows the ratio (mm/kW) of the outer diameter of the main gas pipe 30a or the main liquid pipe 40a to the cooling capacity of the outdoor unit 10A.
- the outdoor unit 10A When a plurality of indoor units 20A, 20B, and 20C are coupled to one outdoor unit 10A as in the heat pump apparatus 200, the outdoor unit 10A often has a cooling capacity of more than 10 kW.
- the outer diameters of the main gas pipe 30a and the main liquid pipe 40a to be chosen in consideration of the design pressure of the heat pump apparatus 200 that includes the outdoor unit 10A having a cooling capacity of 10 kW or more and less than 40 kW will be described below with reference to Figs. 6 and 7 .
- the main gas pipe 30a When the outdoor unit 10A has a cooling capacity of 10 kW or more and less than 20 kW, the main gas pipe 30a most desirably has an outer diameter of 19.1, 22.2, or 25.4 mm (corresponding to “double circle"), more desirably 15.9, 28.6, or 31.8 mm (corresponding to "circle”), desirably 34.9 mm (corresponding to "triangle").
- the main gas pipe 30a When the outdoor unit 10A has a cooling capacity of 20 kW or more and less than 30 kW, the main gas pipe 30a most desirably has an outer diameter of 22.2, 25.4, or 28.6 mm (corresponding to "double circle"), more desirably 15.9, 19.1, 31.8, or 34.9 mm (corresponding to "circle").
- the main gas pipe 30a When the outdoor unit 10A has a cooling capacity of 30 kW or more and less than 40 kW, the main gas pipe 30a most desirably has an outer diameter of 25.4, 28.6, or 31.8 mm (corresponding to “double circle”), more desirably 19.1, 22.2, or 34.9 mm (corresponding to "circle”), desirably 15.9 mm (corresponding to "triangle").
- the main liquid pipe 40a When the outdoor unit 10A has a cooling capacity of 10 kW or more and less than 20 kW, the main liquid pipe 40a most desirably has an outer diameter of 9.52 or 12.7 mm (corresponding to "double circle"), more desirably 6.35 or 15.9 mm (corresponding to "circle”), desirably 19.1 mm (corresponding to "triangle").
- the main liquid pipe 40a When the outdoor unit 10A has a cooling capacity of 20 kW or more and less than 30 kW, the main liquid pipe 40a most desirably has an outer diameter of 12.7 mm (corresponding to "double circle"), more desirably 6.35, 9.52, 15.9, or 19.1 mm (corresponding to "circle").
- the main liquid pipe 40a When the outdoor unit 10A has a cooling capacity of 30 kW or more and less than 40 kW, the main liquid pipe 40a most desirably has an outer diameter of 12.7 or 15.9 mm (corresponding to "double circle"), more desirably 9.52 or 19.1 mm (corresponding to "circle”), desirably 6.35 mm (corresponding to "triangle").
- Fig. 7 shows the ratios (mm/kW) of the outer diameters of the main gas pipe 40a and the main liquid pipe 40a to cooling capacity.
- the ratio (mm/kW) of the outer diameter of the main gas pipe 30a to cooling capacity desirably ranges from 0.40 to 3.49 (corresponding to “double circle”, “circle”, or “triangle"), more desirably 0.48 to 3.18 (corresponding to “double circle” or “circle”), most desirably 0.64 to 2.54 (corresponding to "double circle”).
- the outer diameter of the main gas pipe 30a is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of the outdoor unit 10 ranges from 0.40 to 3.49.
- the ratio (mm/kW) of the outer diameter of the main liquid pipe 40a to cooling capacity desirably ranges from 0.16 to 1.91 (corresponding to “double circle”, “circle”, or “triangle"), more desirably 0.24 to 1.59 (corresponding to “double circle” or “circle”), most desirably 0.32 to 1.27 (corresponding to "double circle”).
- the outer diameter of the main liquid pipe 40a is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of the outdoor unit 10 ranges from 0.16 to 1.91.
- an HFC refrigerant particularly HFO-1234yf in the case of HFO refrigerants or HFC32 in the case of HFC refrigerants, is mixed to suppress the decomposition reaction of HFO-1123.
- the optimum outer diameters of pipes to be used as the main gas pipe 30a and the main liquid pipe 40a can be chosen on the assumption that the decomposition reaction of HFO-1123 is suppressed, and this can reduce the cost of the heat pump apparatus 200.
- a heat pump apparatus 300 described in Embodiment 3 includes a plurality of indoor units coupled to two outdoor units.
- the heat pump apparatus 300 includes three indoor units 20A, 20B, and 20C coupled to two outdoor units 10A and 10B.
- the outdoor units 10A and 10B include no expansion valve, and the indoor units 20A, 20B, and 20C include expansion valves 24a, 24b, and 24c, respectively.
- the gas pipes of the heat pump apparatus 300 are composed of a gas pipe 33a, a gas pipe 33b, a main gas pipe 30b, a gas pipe 31, a gas pipe 32a, and a gas pipe 32c.
- the liquid pipes of the heat pump apparatus 300 are composed of a liquid pipe 43a, a liquid pipe 43b, a main liquid pipe 40b, a liquid pipe 41, a liquid pipe 42a, a liquid pipe 42b, and a liquid pipe 42c.
- the gas pipe 33a, the gas pipe 33b, the main gas pipe 30b, the gas pipe 31, the gas pipe 32a, and the gas pipe 32c are coupled together with a branch joint 60, a branch joint 50a, and a branch joint 50b.
- the liquid pipe 43a, the liquid pipe 43b, the main liquid pipe 40b, the liquid pipe 41, the liquid pipe 42a, the liquid pipe 42b, and the liquid pipe 42c are coupled together with a branch joint 65, a branch joint 55a, and a branch joint 55b.
- the branch joint 60 and the branch joint 65 are three-way branch joints each having opening ports in three directions.
- the three opening ports of the branch joint 50a are coupled to the main gas pipe 30b, the gas pipe 31, and the gas pipe 32a.
- the three opening ports of the branch joint 50b are coupled to the gas pipe 31, the gas pipe 32c, and the gas pipe 32b.
- the three opening ports of the branch joint 55a are coupled to the main liquid pipe 40b, the liquid pipe 41, and the liquid pipe 42a.
- the three opening ports of the branch joint 55b are coupled to the liquid pipe 41, the liquid pipe 42c, and the liquid pipe 42b.
- the three opening ports of the branch joint 60 are coupled to the main gas pipe 30b, the gas pipe 33a, and the gas pipe 33b.
- the three opening ports of the branch joint 65 are coupled to the main liquid pipe 40b, the liquid pipe 43a, and the liquid pipe 43b.
- the gas pipe 32a is coupled to a gas pipe joint 22a of the indoor unit 20A
- the gas pipe 32b is coupled to the gas pipe joint 22b of the indoor unit 20B
- the gas pipe 32c is coupled to the gas pipe joint 22c of the indoor unit 20C.
- the liquid pipe 42a is coupled to the liquid pipe joint 23a of the indoor unit 20A
- the liquid pipe 42b is coupled to the liquid pipe joint 23b of the indoor unit 20B
- the liquid pipe 42c is coupled to the liquid pipe joint 23c of the indoor unit 20C.
- a high-temperature high-pressure gas refrigerant discharged from the compressor 12a of the outdoor unit 10A flows into a four-way valve 13a.
- the high-temperature high-pressure gas refrigerant flows from the four-way valve 13a to the gas pipe joint 16a, the gas pipe 33a, the branch joint 60, the main gas pipe 30b, and the branch joint 50a.
- the refrigerant is divided by the branch joint 50a into the gas pipe 32a and the gas pipe 31.
- the refrigerant flowing through the gas pipe 31 is divided by the branch joint 50b into the gas pipe 32b and the gas pipe 32c.
- the high-temperature high-pressure gas refrigerant flows through the gas pipes 32a, 32b, and 32c and the gas pipe joint 22a, the gas pipe joint 22b, and the gas pipe joint 22c into indoor heat exchangers 21 a, 21 b, and 21 c of the indoor units 20A, 20B, and 20C.
- the high-temperature high-pressure gas refrigerant exchanges heat in the indoor heat exchangers 21 a, 21 b, and 21 c and becomes a low-temperature high-pressure liquid refrigerant, and is depressurized by the expansion valves 24a, 24b, and 24c and becomes a low-temperature high-pressure two-phase gas-liquid refrigerant.
- a high-temperature high-pressure gas refrigerant discharged from the compressor 12b of the outdoor unit 10B flows through the gas pipe joint 16b and the gas pipe 33b and joins the refrigerant flowing from the outdoor unit 10A at the branch joint 60.
- the low-temperature high-pressure two-phase gas-liquid refrigerant from the expansion valve 24a flows through the liquid pipe 42a, the branch joint 55a, the main liquid pipe 40b, the branch joint 65, the liquid pipe 43a, and the liquid pipe joint 17a into an outdoor heat exchanger 14a.
- a refrigerant branched off at the branch joint 65 flows through the liquid pipe 43b and the liquid pipe joint 17b into an outdoor heat exchanger 14b.
- the low-temperature high-pressure two-phase gas-liquid refrigerant from the expansion valve 24b flows through the liquid pipe 42b, the branch joint 55b, the liquid pipe 41, the branch joint 55a, the main liquid pipe 40b, the branch joint 65, the liquid pipe 43a, and the liquid pipe joint 17a into the outdoor heat exchanger 14a.
- a refrigerant branched off at the branch joint 65 flows through the liquid pipe 43b and the liquid pipe joint 17b into the outdoor heat exchanger 14b.
- the low-temperature high-pressure two-phase gas-liquid refrigerant from the expansion valve 24c flows through the liquid pipe 42c, the branch joint 55b, the liquid pipe 41, the branch joint 55a, the main liquid pipe 40b, the branch joint 65, the liquid pipe 43a, and the liquid pipe joint 17a into the outdoor heat exchanger 14a.
- a refrigerant branched off at the branch joint 65 flows through the liquid pipe 43b and the liquid pipe joint 17b into an outdoor heat exchanger 14b.
- the low-temperature high-pressure two-phase gas-liquid refrigerant exchanges heat with outdoor air in the outdoor heat exchanger 14a and becomes a high-temperature low-pressure gas refrigerant.
- the high-temperature low-pressure gas refrigerant from the outdoor heat exchanger 14a flows through the four-way valve 13a into an accumulator 11 a.
- the low-temperature high-pressure two-phase gas-liquid refrigerant exchanges heat with outdoor air in the outdoor heat exchanger 14b and becomes a high-temperature low-pressure gas refrigerant.
- the high-temperature low-pressure gas refrigerant from the outdoor heat exchanger 14b flows through the four-way valve 13b into an accumulator 11 b.
- the high-temperature high-pressure gas refrigerant exchanges heat with outdoor air in the outdoor heat exchanger 14a and becomes a low-temperature high-pressure liquid refrigerant.
- the low-temperature high-pressure liquid refrigerant from the outdoor heat exchanger 14a flows through the liquid pipe joint 17a, the liquid pipe 43a, the branch joint 65, and the main liquid pipe 40b into the branch joint 55a.
- the refrigerant is divided by the branch joint 55a into the liquid pipe 41 and the liquid pipe 42a.
- the refrigerant flowing through the liquid pipe 41 is divided by the branch joint 55b into the liquid pipe 42b and the liquid pipe 42c.
- the low-temperature high-pressure liquid refrigerant flows through the liquid pipe 42a, the liquid pipe 42b, and the liquid pipe 42c and the liquid pipe joint 23a, the liquid pipe joint 23b, and the liquid pipe joint 23c into the expansion valve 24a, the expansion valve 24b, and the expansion valve 24c.
- the low-temperature high-pressure liquid refrigerant are depressurized by the expansion valve 24a, the expansion valve 24b, and the expansion valve 24c and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant.
- the low-temperature low-pressure two-phase gas-liquid refrigerant from the expansion valve 24a, the expansion valve 24b, and the expansion valve 24c flows into the indoor heat exchanger 21 a, the indoor heat exchanger 21 b, and the indoor heat exchanger 21 c, exchanges heat with indoor air, and becomes a high-temperature low-pressure gas refrigerant.
- the high-temperature high-pressure gas refrigerant exchanges heat with outdoor air in the outdoor heat exchanger 14b and becomes a low-temperature high-pressure liquid refrigerant.
- the low-temperature high-pressure liquid refrigerant from the outdoor heat exchanger 14b flows through the liquid pipe joint 17b and the liquid pipe 43b and joins the refrigerant flowing from the outdoor unit 10A at the branch joint 65.
- the high-temperature low-pressure gas refrigerant from the indoor heat exchanger 21 a flows through the gas pipe joint 22a, the gas pipe 32a, the branch joint 50a, the main gas pipe 30b, and the branch joint 60.
- the high-temperature low-pressure gas refrigerant from the indoor heat exchanger 21 b flows through the gas pipe joint 22b, the gas pipe 32b, the branch joint 50b, the gas pipe 31, the branch joint 50a, the main gas pipe 30b, and the branch joint 60.
- the high-temperature low-pressure gas refrigerant from the indoor heat exchanger 21 c flows through the gas pipe joint 22c, the gas pipe 32c, the gas pipe 32c, the branch joint 50b, the gas pipe 31, the branch joint 50a, the main gas pipe 30b, and the branch joint 60.
- the high-temperature low-pressure gas refrigerant is divided by the branch joint 60 into the gas pipe 33a and the gas pipe 33b.
- the high-temperature low-pressure gas refrigerant flowing through the gas pipe 33a flows through the gas pipe joint 16a and the four-way valve 13a into the accumulator 11 a.
- the high-temperature low-pressure gas refrigerant flowing through the gas pipe 33b flows through the gas pipe joint 16b and the four-way valve 13b into the accumulator 11 b.
- a high-temperature high-pressure gas refrigerant flows through the main gas pipe 30b, and in cooling operation, a high-temperature low-pressure gas refrigerant flows through the main gas pipe 30b.
- a low-temperature high-pressure two-phase gas-liquid refrigerant flows through the main liquid pipe 40b, and in cooling operation, low-temperature high-pressure liquid refrigerant flows through the main liquid pipe 40b.
- the outer diameter and thickness of the gas pipe 30b and the liquid pipe 40b satisfy the following conditions.
- the amount of refrigerant flowing through the main gas pipe 30a into the gas pipe 31 is decreased by the amount of refrigerant flowing through the branch joints 50a and 55a into the indoor unit 20A.
- the gas pipe 31 can have a smaller outer diameter and thickness than the main gas pipe 30a.
- Refrigerant from the outdoor unit 10A and refrigerant from the outdoor unit 10B come together at the branch joints 60 and 65, thus increasing the refrigerant flow rate in the main gas pipe 30b and the main liquid pipe 40b.
- the main gas pipe 30b and the main liquid pipe 40b must therefore have a larger outer diameter and thickness than the gas pipes 33a and 33b and the liquid pipes 43a and 43b.
- Fig. 9 shows the outer diameters ⁇ (mm) of the main gas pipe 30b and the main liquid pipe 40b usable depending on the cooling capacities of the outdoor unit 10A and the outdoor unit 10B according to Embodiment 3.
- Fig. 10 shows the ratios (mm/kW) of the outer diameters of the main gas pipe 30b and the main liquid pipe 40b to the total cooling capacity of the outdoor unit 10A and the outdoor unit 10B.
- the outdoor unit 10B As well as the outdoor unit 10A is coupled to the indoor units 20A, 20B, and 20C.
- the design pressure depends on the total cooling capacity of the outdoor unit 10A and the outdoor unit 10B.
- the outer diameter and thickness of the main gas pipe 30b and the main liquid pipe 40b can be chosen on the basis of the total cooling capacity of the outdoor unit 10A and the outdoor unit 10B.
- the total cooling capacity of the outdoor unit 10A having a cooling capacity of 20 kW and the outdoor unit 10B having a cooling capacity of 30 kW is 50 kW.
- Fig. 10 shows the ratios (mm/kW) of the outer diameters of the main gas pipe 40a and the main liquid pipe 40a to cooling capacity.
- the ratio (mm/kW) of the outer diameter of the main gas pipe 30b to cooling capacity desirably ranges from 0.32 to 1.11 (corresponding to “double circle”, “circle”, or “triangle"), more desirably 0.36 to 1.03 (corresponding to “double circle” or “circle”), most desirably 0.41 to 1.03 (corresponding to “double circle”).
- the outer diameter of the main gas pipe 30b is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of the outdoor unit 10 ranges from 0.32 to 1.11.
- the ratio (mm/kW) of the outer diameter of the main liquid pipe 40b to cooling capacity desirably ranges from 0.14 to 0.56 (corresponding to “double circle”, “circle”, or “triangle"), more desirably 0.16 to 0.48 (corresponding to “double circle” or “circle”), most desirably 0.23 to 0.40 (corresponding to "double circle”).
- the outer diameter of the main liquid pipe 40a is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of the outdoor unit 10 ranges from 0.14 to 1.56.
- the heat pump apparatus 300 described in Embodiment 3 includes three indoor units 20A, 20B, and 20C coupled to two outdoor units 10A and 10B, the number of indoor units may be more than three.
- Each of the gas pipe 32c and the liquid pipe 42c is provided with an additional branch joint, and the branch joint is coupled to a gas pipe and a liquid pipe.
- the gas pipe and liquid pipe are coupled to an indoor unit. In this manner, an indoor unit can be added by retrofitting a gas pipe and a liquid pipe with a branch joint.
- each of the main gas pipe 30b and the main liquid pipe 40b is provided with an additional branch joint, and the branch joint is coupled to a gas pipe and a liquid pipe.
- the gas pipe and liquid pipe are coupled to an indoor unit.
- Fig. 11 shows the outer diameters ⁇ (mm) of a main gas pipe and a main liquid pipe in the case that a plurality of outdoor units have a total cooling capacity of 70 kW or more.
- Fig. 12 shows the ratios (mm/kW) of the outer diameters of a main gas pipe and a main liquid pipe to the total cooling capacity of a plurality of outdoor units. For example, the total cooling capacity of three outdoor units each having a cooling capacity of 30 kW is 90 kW.
- Fig. 12 shows the ratios (mm/kW) of the outer diameters of a main gas pipe and a main liquid pipe to cooling capacity.
- the ratio (mm/kW) of the outer diameter of the main gas pipe to cooling capacity desirably ranges from 0.25 to 0.73 (corresponding to “double circle”, “circle”, or “triangle"), more desirably 0.28 to 0.64 (corresponding to “double circle” or “circle”), most desirably 0.38 to 0.59 (corresponding to "double circle”).
- the outer diameter of a main gas pipe is chosen such that the ratio (mm/kW) of the outer diameter to the total cooling capacity of outdoor units ranges from 0.25 to 0.73.
- the ratio (mm/kW) of the outer diameter of a main liquid pipe to cooling capacity desirably ranges from 0.13 to 0.36 (corresponding to “double circle”, “circle”, or “triangle"), more desirably 0.14 to 0.32 (corresponding to “double circle” or “circle”), most desirably 0.19 to 0.28 (corresponding to "double circle”).
- the outer diameter of a main liquid pipe is chosen such that the ratio (mm/kW) of the outer diameter to the total cooling capacity of outdoor units ranges from 0.13 to 0.36.
- an HFC refrigerant particularly HFO-1234yf in the case of HFO refrigerants or HFC32 in the case of HFC refrigerants, is mixed to suppress the decomposition reaction of HFO-1123.
- the optimum outer diameters of pipes to be used as the main gas pipe 30b and the main liquid pipe 40b can be chosen on the assumption that the decomposition reaction of HFO-1123 is suppressed, and this can reduce the cost of the heat pump apparatus 300.
- a pipe having an outer diameter in the range of 6.35 to 12.7 mm be made of an O-material having a thickness of 0.8 mm or more.
- a pipe having an outer diameter of 15.9 mm is preferably made of an O-material having a thickness of 1.0 mm or more.
- a pipe having an outer diameter in the range of 19.1 to 28.6 mm be made of a 1/2H-material having a thickness of 1.0 mm or more.
- a pipe having an outer diameter of 31.8 mm be made of a 1/2H-material having a thickness of 1.1 mm or more.
- a pipe having an outer diameter of 34.9 mm be made of a 1/2H-material having a thickness of 1.2 mm or more.
- a pipe having an outer diameter of 38.1 mm be made of a 1/2H-material having a thickness of 1.35 mm or more.
- a pipe having an outer diameter of 41.3 mm be made of a 1/2H-material having a thickness of 1.45 mm or more.
- a pipe having an outer diameter of 44.5 mm be made of a 1/2H-material having a thickness of 1.55 mm or more.
- a pipe having an outer diameter in the range of 50.8 to 54.0 mm be made of a 1/2H-material having a thickness of 1.80 mm or more.
- O-materials are "materials in the softest state after annealing", and 1/2H-materials are "materials work hardened by cold working”.
- the upper limit of the thickness is 1.3 times the lower limit of the thickness.
- the lower limit of the thickness is 0.8 mm
- the upper limit of the thickness is 1.04 mm (0.8 mm x 1.3).
- the thickness of a pipe having an outer diameter of 6.35 mm ranges from 0.8 to 10.4 mm.
- pipes widely used with R410A have a thickness chosen as described above for their outer diameters, the pipes can be applied to heat pump apparatus in which HFO-1123 and an HFC refrigerant circulate. This obviates the need to produce a special pipe having a large thickness designed for HFO-1123. Thus, a heat pump apparatus can be produced without increased pipe costs.
- gas pipe refers to a pipe through which a high-temperature high-pressure gas refrigerant discharged from a compressor flows before entering a condenser.
- liquid pipe refers to a pipe through which a low-temperature high-pressure liquid refrigerant from an evaporator or a low-temperature low-pressure two-phase gas-liquid refrigerant passing through an expansion valve flows.
- main gas pipe and “main gas pipe” in Embodiments 2 and 3 refer to a gas pipe and a liquid pipe having the largest outer diameter out of a plurality of gas pipes coupled with a branch joint.
- the outer diameter of a pipe coupled to a branch joint at which refrigerant from an outdoor unit or indoor unit joins is larger than the outer diameters of pipes coupled to a gas pipe joint and a liquid pipe joint of a particular outdoor unit.
- a pipe having the largest outer diameter is referred to as a main pipe.
- a heat pump apparatus may include an intermediate device in which an outdoor unit is coupled to an intermediate unit, and the intermediate unit is coupled to an indoor unit.
- the intermediate device includes an intermediate heat exchanger, and refrigerant from an outdoor unit exchanges heat with a heat medium, such as water or brine, in the intermediate heat exchanger. After heat exchange with the refrigerant, the heat medium flows into an indoor unit. The refrigerant does not flow into the indoor unit.
- a heat pump apparatus including an intermediate device, a gas pipe and a liquid pipe refers to pipes between an outdoor unit and the intermediate device.
- a heat pump apparatus in which refrigerant circulates between an indoor unit and an outdoor unit includes “a heat pump apparatus equipped with an intermediate unit in which refrigerant circulates between the intermediate unit and an outdoor unit”, including a heat pump apparatus in which a heat medium, such as water or brine, rather than refrigerant, flows into an indoor unit.
- a heat medium such as water or brine
- ester lubricating oil and ether lubricating oil will be described below.
- ester lubricating oil examples include dibasic acid ester oil, polyol ester oil, complex ester oil, and polyol carbonate oil.
- the dibasic acid ester oil is preferably an ester between a dibasic acid having 5 to 10 carbon atoms (glutaric acid, adipic acid, pimelic acid, suberic acid, azelaic acid, or sebacic acid) and a monohydric alcohol having a linear or branched alkyl group and having 1 to 15 carbon atoms (methanol, ethanol, propanol, butanol, pentanol, hexanol, heptanol, octanol, nonanol, decanol, undecanol, dodecanol, tridecanol, tetradecanol, or pentadecanol).
- a dibasic acid having 5 to 10 carbon atoms (glutaric acid, adipic acid, pimelic acid, suberic acid, azelaic acid, or sebacic acid)
- a monohydric alcohol having a linear or branched alkyl group and having
- the dibasic acid ester oil is ditridecyl glutarate, di(2-ethylhexyl) adipate, diisodecyl adipate, ditridecyl adipate, or di(3-ethylhexyl) sebacate.
- the polyol ester oil is preferably an ester between a diol (ethylene glycol, 1,3-propanediol, propylene glycol, 1,4-butanediol, 1,2-butanediol, 1,5-pentadiol, neopentyl glycol, 1,7-heptanediol, or 1,12-dodecanediol) or a polyol having 3 to 20 hydroxy groups (trimethylolethane, trimethylolpropane, trimethylolbutane, pentaerythritol, glycerin, sorbitol, sorbitan, or a sorbitol glycerin condensate) and a fatty acid having 6 to 20 carbon atoms (a linear or branched fatty acid, such as hexanoic acid, heptanoic acid, octanoic acid, nonanoic acid, decanoic acid,
- the polyol ester oil may have a free hydroxy group.
- the polyol ester oil is preferably an ester (trimethylolpropane tripelargonate, pentaerythritol 2-ethylhexanoate, or pentaerythritol tetrapelargonate) of a hindered alcohol (neopentyl glycol, trimethylolethane, trimethylolpropane, trimethylolbutane, or pentaerythritol).
- a hindered alcohol neopentyl glycol, trimethylolethane, trimethylolpropane, trimethylolbutane, or pentaerythritol
- the complex ester oil refers to an ester between a fatty acid and a dibasic acid and a monohydric alcohol and a polyol.
- the fatty acid, dibasic acid, monohydric alcohol, and polyol may be those described above.
- the polyol carbonate oil refers to an ester between carbonic acid and a polyol.
- the polyol may be a diol or polyol described above.
- the polyol carbonate oil may be a product of ring-opening polymerization of a cyclic alkylene carbonate.
- the ether lubricating oil may be a poly(vinyl ether) oil or a polyoxyalkylene lubricating oil.
- the poly(vinyl ether) oil may be a polymerization product of a vinyl ether monomer, such as an alkyl vinyl ether, or a copolymer of a vinyl ether monomer and a hydrocarbon monomer having an olefinic double bond.
- vinyl ether monomers may be used alone or in combination.
- hydrocarbon monomer having an olefinic double bond examples include ethylene, propylene, butenes, pentenes, hexenes, heptenes, octenes, diisobutylene, triisobutylene, styrene, ⁇ -methylstyrene, and alkyl substituted styrenes. These hydrocarbon monomers having an olefinic double bond may be used alone or in combination.
- the poly(vinyl ether) copolymer may be a block or random copolymer.
- poly(vinyl ether)s may be used alone or in combination.
- the present invention can be utilized in air-conditioning apparatus and freezing devices that utilize a heat pump cycle.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Organic Chemistry (AREA)
- Combustion & Propulsion (AREA)
- Materials Engineering (AREA)
- General Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
It is an object of the present invention to provide an inexpensive heat pump apparatus in which HFO-1123 circulates.
The present invention provides a heat pump apparatus in which refrigerant circulates between an indoor unit and an outdoor unit, wherein the refrigerant is a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123, the outdoor unit has a cooling capacity (kW) in the range of 2.2 to 9.5 kW, the outer diameter φ (mm) of a gas pipe between the indoor unit and the outdoor unit and the cooling capacity (kW) of the outdoor unit satisfy the relation (1.00 ≤ outer diameter φ (mm) of gas pipe/cooling capacity (kW) of outdoor unit ≤ 5.77), and the outer diameter φ (mm) of a liquid pipe between the indoor unit and the outdoor unit and the cooling capacity (kW) of the outdoor unit satisfy the relation (0.67 ≤ outer diameter φ (mm) of liquid pipe/cooling capacity (kW) of outdoor unit ≤ 5.77).
Description
- The present invention relates to an air-conditioning apparatus to which a refrigerant having lower global warming potential (GWP) than R410A is applied.
- Known air-conditioning apparatus utilize heat pump cycles with HFC refrigerant R410A. As global warming has become an increasingly serious environmental issue, however, refrigerants having lower global warming potential than R410A are being developed. Refrigerants with lower GWP than R410A (GWP: 2000) may be HFC32 (difluoromethane), HFO-1234yf (2,3,3,3-tetrafluoropropane), and HFO-1123 (1,1,2-trifluoroethylene).
- HFO stands for hydrofluoroolefin, and HFC stands for hydrofluorocarbon.
- In particular, HFO-1123 (GWP100: 0.3) has lower GWP than HFC32 (GWP100: 675) and HFO-1234yf (GWP100: 4). Thus, in view of global warming issues, air-conditioning apparatus that utilize HFO-1123 are under study.
- Patent Literature 1: International Publication No.
WO 2012/157764 A1 - However, a decomposition reaction of HFO-1123 may induce a subsequent series of decomposition reactions. To withstand pressure increase in a refrigerant pipe caused by the series of decomposition reactions, the outer diameter of the refrigerant pipe must be increased to reduce the pressure in the refrigerant pipe. However, an increased outer diameter of refrigerant pipes results in increased costs of the refrigerant pipes.
- It is an object of the present invention to provide an inexpensive air-conditioning apparatus to which HFO-1123 is applied.
- The present invention provides a heat pump apparatus including:
- an indoor unit;
- an outdoor unit having a cooling capacity (kW) in the range of 2.2 to 9.5 kW;
- a refrigerant circulating between the indoor unit and the outdoor unit, the refrigerant being a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123;
- a gas pipe communicating between the indoor unit and the outdoor unit; and
- a liquid pipe communicating between the indoor unit and the outdoor unit,
- (1) 1.00 ≤ an outer diameter φ (mm) of the gas pipe/the cooling capacity (kW) of the outdoor unit ≤ 5.77
- (2) 0.67 ≤ an outer diameter φ (mm) of the liquid pipe/the cooling capacity (kW) the of outdoor unit ≤ 5.77
- The present invention provides heat pump apparatus including
- a plurality of indoor units;
- at least one outdoor unit having a cooling capacity (kW) of 10 kW or more and less than 40 kW;
- a refrigerant circulating between the plurality of indoor units and the at least one outdoor unit, the refrigerant being a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123;
- a main gas pipe communicating between the plurality of indoor units and the at least one outdoor unit; and
- a main liquid pipe communicating between the plurality of indoor units and the at least one outdoor unit,
- (1) 0.40 ≤ an outer diameter φ (mm) of the main gas pipe/the cooling capacity (kW) of the at least one outdoor unit ≤ 3.49
- (2) 0.16 ≤ an outer diameter φ (mm) of the main liquid pipe/the cooling capacity (kW) of the at least one outdoor unit ≤ 1.91
- The present invention provides a heat pump apparatus including:
- a plurality of indoor units;
- at least two outdoor units, the at least two outdoor units having a total cooling capacity (kW) of 40 kW or more and less than 70 kW;
- a refrigerant circulating between the plurality of indoor units and the at least two outdoor units, the refrigerant being a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123;
- a main gas pipe communicating between the plurality of indoor units and the at least two outdoor units; and
- a main liquid pipe comunicating between the plurality of indoor units and the at least two outdoor units,
- (1) 0.32 ≤ an outer diameter φ (mm) of the main gas pipe/ the total cooling capacity (kW) of the at least two outdoor units ≤ 1.11
- (2) 0.14 ≤ an outer diameter φ (mm) of the main liquid pipe/cooling capacity (kW) of the at least two outdoor units ≤ 0.56
- The present invention provides a heat pump apparatus including:
- a plurality of indoor units;
- at least three outdoor units having a total cooling capacity (kW) of 70 kW or more and less than 100 kW;
- a refrigerant circulating between the plurality of indoor units and the at least three outdoor units, the refrigerant being a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123;
- a main gas pipe communicating between the plurality of indoor units and the at least three outdoor units; and
- a liquid pipe communicating between the plurality of indoor units and the at least three outdoor units,
- (1) 0.25 ≤ an outer diameter φ (mm) of the main gas pipe /the total cooling capacity (kW) of the plurality of indoor units ≤ 0.73
- (2) 0.13 ≤ an outer diameter φ (mm) of the liquid pipe /the total cooling capacity (kW) of the plurality of indoor units ≤ 0.36
- The present invention can provide an inexpensive air-conditioning apparatus that utilizes HFO-1123 by using gas pipes and liquid pipes depending on the cooling capacity of an outdoor unit.
-
- [
Fig. 1] Fig. 1 is a refrigerant circuit diagram of aheat pump apparatus 100 according toEmbodiment 1. - [
Fig. 2] Fig. 2 is a chemical formula of a decomposition reaction of HFO-1123. - [
Fig. 3] Fig. 3 is a table showing the relationship between cooling capacity and the types of gas pipes and liquid pipes usable in theheat pump apparatus 100 according toEmbodiment 1. - [
Fig. 4] Fig. 4 is a table showing the relationship of the outer diameter φ (mm) of gas pipes and liquid pipes/cooling capacity (kW) in theheat pump apparatus 100 according toEmbodiment 1. - [
Fig. 5] Fig. 5 is a refrigerant circuit diagram of aheat pump apparatus 200 according to Embodiment 2. - [
Fig. 6] Fig. 6 is a table showing the relationship between cooling capacity and the types of gas pipes and liquid pipes usable in theheat pump apparatus 200 according to Embodiment 2. - [
Fig. 7] Fig. 7 is a table showing the relationship of the outer diameter φ (mm) of gas pipes and liquid pipes/cooling capacity (kW) in theheat pump apparatus 200 according to Embodiment 2. - [
Fig. 8] Fig. 8 is a refrigerant circuit diagram of aheat pump apparatus 300 according to Embodiment 3. - [
Fig. 9] Fig. 9 is a table showing the relationship between cooling capacity and the types of gas pipes and liquid pipes usable in theheat pump apparatus 300 according to Embodiment 3. - [
Fig. 10] Fig. 10 is a table showing the relationship of the outer diameter φ (mm) of gas pipes and liquid pipes/cooling capacity (kW) in theheat pump apparatus 300 according to Embodiment 3. - [
Fig. 11] Fig. 11 is a table showing the relationship between cooling capacity and the types of gas pipes and liquid pipes usable in another embodiment of the heat pump apparatus according to Embodiment 3. - [
Fig. 12] Fig. 12 is a table showing the relationship of the outer diameter φ (mm) of gas pipes and liquid pipes/cooling capacity (kW) in another embodiment of the heat pump apparatus according to Embodiment 3. - In the present invention (
Embodiments 1 to 3), hydrofluorocarbon (HFC) refrigerants are hydrocarbons having fluorine (F) and no chlorine (CI) in their molecular structures. Hydrofluoroolefin (HFO) refrigerants are hydrocarbons having fluorine and no chlorine in their molecular structures and further have a carbon-carbon double bond. HFO refrigerants are included in HFC refrigerants. -
Fig. 1 illustrates a refrigerant circuit of aheat pump apparatus 100 according toEmbodiment 1. The refrigerant circuit of theheat pump apparatus 100 will be described below with reference toFig. 1 . - The
heat pump apparatus 100 is an air-conditioning apparatus that can be switched between cooling operation and heating operation. - The
heat pump apparatus 100 includes anoutdoor unit 10 and anindoor unit 20. Theoutdoor unit 10 is placed outdoors, and theindoor unit 20 is placed in a room to be air-conditioned. Theoutdoor unit 10 includes anaccumulator 11, acompressor 12, a four-way valve 13, anoutdoor heat exchanger 14, a gas pipe joint 16, and a liquid pipe joint 17. Theindoor unit 20 includes anindoor heat exchanger 21, a gas pipe joint 22, and a liquid pipe joint 23. Theoutdoor unit 10 and theindoor unit 20 are connected through thegas pipe 30 and theliquid pipe 40. Thegas pipe 30 is coupled to the gas pipe joint 16 and the gas pipe joint 22. Theliquid pipe 40 is connected to the liquid pipe joint 17 and the liquid pipe joint 23. - The
accumulator 11 contains liquid refrigerant and gas refrigerant. The gas refrigerant is sucked into thecompressor 12. High-temperature low-pressure gas refrigerant sucked into thecompressor 12 is compressed and is discharged as a high-temperature high-pressure gas refrigerant. - The refrigerant flow path can be changed with the four-
way valve 13 to switch between a flow path for cooling operation and a flow path for heating operation. - Although the
heat pump apparatus 100 according toEmbodiment 1 includes theaccumulator 11, theaccumulator 11 is not necessarily required. - First, a refrigerant flow in heating operation will be described below. A high-temperature high-pressure gas refrigerant discharged from the
compressor 12 flows into the four-way valve 13. The high-temperature high-pressure gas refrigerant flows through the four-way valve 13, the gas pipe joint 16, thegas pipe 30, and the gas pipe joint 22 into theindoor heat exchanger 21. The high-temperature high-pressure gas refrigerant exchanges heat with indoor air in theindoor heat exchanger 21 and becomes a low-temperature high-pressure liquid refrigerant. The low-temperature high-pressure liquid refrigerant from theindoor heat exchanger 21 flows through the liquid pipe joint 23, theliquid pipe 40, and the liquid pipe joint 17 into anexpansion valve 15. The low-temperature high-pressure liquid refrigerant is depressurized by theexpansion valve 15 and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant. The low-temperature low-pressure two-phase gas-liquid refrigerant from theexpansion valve 15 flows into theoutdoor heat exchanger 14. The low-temperature low-pressure two-phase gas-liquid refrigerant exchanges heat with outdoor air in theoutdoor heat exchanger 14 and becomes a high-temperature low-pressure gas refrigerant. The high-temperature low-pressure gas refrigerant from theoutdoor heat exchanger 14 flows through the four-way valve 13 into theaccumulator 11. - Next, a refrigerant flow in cooling operation will be described below. A high-temperature high-pressure gas refrigerant discharged from the
compressor 12 flows through the four-way valve 13 into theoutdoor heat exchanger 14. The high-temperature high-pressure gas refrigerant exchanges heat with outdoor air in theoutdoor heat exchanger 14 and becomes a low-temperature high-pressure liquid refrigerant. The low-temperature high-pressure liquid refrigerant from theoutdoor heat exchanger 14 flows into theexpansion valve 15. The low-temperature high-pressure liquid refrigerant is depressurized by theexpansion valve 15 and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant. The low-temperature low-pressure two-phase gas-liquid refrigerant from theexpansion valve 15 flows through the liquid pipe joint 17, theliquid pipe 40, and the liquid pipe joint 23 into theindoor heat exchanger 21. The low-temperature low-pressure two-phase gas-liquid refrigerant exchanges heat with indoor air in theindoor heat exchanger 21 and becomes a high-temperature low-pressure gas refrigerant. The high-temperature low-pressure gas refrigerant from theindoor heat exchanger 21 flows through the gas pipe joint 22, thegas pipe 30, the gas pipe joint 16, and the four-way valve 13 into theaccumulator 11. - In heating operation, a high-temperature high-pressure gas refrigerant flows through the
gas pipe 30, and in cooling operation, a high-temperature low-pressure gas refrigerant flows through thegas pipe 30. - In heating operation, low-temperature high-pressure liquid refrigerant flows through the
liquid pipe 40, and in cooling operation, low-temperature low-pressure two-phase gas-liquid refrigerant flows through theliquid pipe 40. - A refrigerant used in the present invention (
Embodiments 1 to 3) will be described below. In the present invention, a refrigerant circulating through the heat pump apparatus is HFO-1123. - HFO-1123 has a GWP100 of 0.4, which is much lower than those of R410A and HFC32, and is preferred in terms of global warming mitigation. When HFO-1123 is applied to heat pump apparatus, however, HFO-1123 may cause a decomposition reaction, and problems resulting from the decomposition reaction must be solved.
-
Fig. 2 shows a decomposition reaction formula of HFO-1123. The decomposition reaction is a disproportionation reaction in which 1 mol of HFO-1123yields 1/2 mol of carbon tetrafluoride (CF4), 2/3 mol of carbon (C), and 1 mol of hydrogen fluoride (HF). The decomposition reaction is also an exothermic reaction in which 1 mol of HFO-1123 generates approximately 45 kcal of heat. - Use of high-purity HFO-1123 may cause a series of decomposition reactions once HFO-1123 decomposes. Thus, a decomposition reaction of HFO-1123 may increase refrigerant pressure beyond expectations in a refrigerant pipe. Furthermore, HFO-1123 is slightly flammable, and leakage of high-temperature HFO-1123 from a pipe may cause a fire.
- A decomposition reaction of HFO-1123 yields hydrogen fluoride (HF). Hydrogen fluoride dissolved in water produces acidic hydrofluoric acid. Hydrofluoric acid may corrode an inner surface of a refrigerant pipe. In particular, the acidity of hydrofluoric acid increases with decreasing temperature. Thus, the
liquid pipe 40 through which a low temperature refrigerant flows may be corroded. - When HFO-1123 is used in heat pump apparatus, therefore, these problems resulting from the decomposition reaction must be addressed; more specifically, pressure increase in refrigerant pipes and corrosion of pipes must be prevented. Although these problems may be addressed by using pipes having a large thickness and outer diameter, use of such pipes undesirably increases the cost of heat pump apparatus.
- In the present invention, a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123 is used to prevent pressure increase in refrigerant pipes and corrosion of pipes. The addition of an HFC refrigerant (other than HFO-1123) to HFO-1123 can suppress the decomposition reaction of HFO-1123 compared with the addition of a natural refrigerant, such as carbon dioxide or propane.
- In particular, the addition of a refrigerant HFO-1234yf or HFC32 to HFO-1123 can further suppress a series of decomposition reactions of HFO-1123 compared with the addition of other HFC refrigerants and HFO refrigerants. It is desirable to add HFC32 rather than HFO-1234yf in view of the energy efficiency of heat pump apparatus.
- Suppression of the decomposition reaction of HFO-1123 can obviate the need to prevent pressure increase in refrigerant pipes and corrosion of pipes.
- In the present invention, a particular refrigerant is mixed with HFO-1123 to prevent the decomposition reaction of HFO-1123, and pipes having an outer diameter optimum for the mixed refrigerant are selected. The outer diameter of selected pipes will be described later.
- In heat pump apparatus, refrigerating machine oil is mixed with refrigerant as lubricating oil for lubricating slide portions of compressors. In the present invention (
Embodiments 1 to 3), it is desirable to use an ether lubricating oil or an ester lubricating oil as a refrigerating machine oil to prevent corrosion of pipes caused by hydrogen fluoride produced by the decomposition reaction of HFO-1123. - In general, ether lubricating oils and ester lubricating oils are hygroscopic and are likely to produce sludge due to hydrolysis, and are therefore sometimes difficult to use in heat pump apparatus in consideration of the reliability of compressors. However, hydrolysis of ether lubricating oils and ester lubricating oils can remove water from pipes and thereby reduce the proportion of hydrogen fluoride that dissolves in water and produces hydrofluoric acid. This can suppress corrosion of pipes caused by hydrogen fluoride.
- Specific examples of ether lubricating oils and ester lubricating oils will be described later.
- The relationship between the pipe diameter of gas pipes and liquid pipes and the cooling capacity of the outdoor unit in the
heat pump apparatus 100 according toEmbodiment 1 will be described below. -
- t: required thickness (mm)
- φ: outer diameter of pipe (mm)
- σa: allowable tensile stress (N/mm2)
- P: design pressure (MPa)
- η: efficiency of welded joint
- The design pressure P refers to a pressure that depends on the type of refrigerant, the amount of refrigerant, and the maximum pressure in refrigerant circuit operation, and provides a standard for the pressure resistance of the product.
- The efficiency η of welded joints is a dimensionless number specified in Japanese Industrial Standards "JIS B 8265 Construction of pressure vessel". For example, welded joints in the form of "one side full thickness fillet welded lap joint without plug welding" have an efficiency η of 0.45.
- For example, in consideration of pressure increase in refrigerant pipes due to heat generated by a series of decomposition reactions, the outer diameter φ of pipes must be larger in the case of HFO-1123 than in the case of R410A, which does not cause a series of decomposition reactions. In consideration of the production of hydrogen fluoride in the decomposition reaction, the required thickness t of pipes must be greater in the case of HFO-1123 than in the case of R410A.
- The design pressure P or the efficiency η of welded joints may be increased to prevent the outer diameter φ and the required thickness t of pipes from being increased. However, a higher design pressure P results in an increased cost of a design change to improve the safety of the
compressor 12. To yield higher efficiency η of welded joints, increased labor costs are necessary, due to a lot of time and effort to perform welding. It may be impossible to increase the efficiency η of welded joints in some welding methods. - Thus, it is desirable that designers design pipes on the assumption that there is no decomposition reaction of HFO-1123.
-
Fig. 3 is a table showing the relationship between cooling capacity and the types of gas pipe and liquid pipe of theheat pump apparatus 100. - The cooling capacity refers to the heat exchange capacity (kW) of the
outdoor unit 10 in cooling operation measured under the following conditions (temperature conditions for mild climatic zone) specified in Japanese Industrial Standards "JIS B 8615-1 ". - Indoor side inlet air temperature: 27 degrees C (dry-bulb temperature), 19 degrees C (wet-bulb temperature)
- Outdoor side inlet air temperature: 35 degrees C (dry-bulb temperature)
-
Fig. 3 shows the outer diameters φ (mm) of thegas pipe 30 and theliquid pipe 40 usable depending on the cooling capacity of theoutdoor unit 10 according toEmbodiment 1. The cooling capacity of theoutdoor unit 10 depends on the performance of thecompressor 12, the size of theoutdoor heat exchanger 14, the amount of refrigerant to be supplied, and other parameters. The design pressure of theheat pump apparatus 100 depends on the cooling capacity of theoutdoor unit 10. InFig. 3 , in consideration of design pressure for a mixed refrigerant of equal weights of HFO-1123 and HFC32, the possible outer diameters of thegas pipe 30 and theliquid pipe 40 are determined on the basis of the mathematical formula (1). It is desirable that the percentage of HFC32 to be mixed be 20% or more by weight and 60% or less by weight. The percentage of HFC32 to be mixed in Embodiments 2 and 3 is the same as inEmbodiment 1. - The symbols in
Fig. 3 (double circle, circle, triangle, and cross) are as follows: - "Double circle" Most desirably used
- "Circle" Desirably used
- "Triangle" Usable
- "Cross" Unusable
- Thus, it is desirable to use the pipes in the order of "double circle" > "circle" > "triangle" > "cross".
- The outer diameters φ (mm) in
Fig. 3 are rounded to three significant figures. Correctly speaking, φ15.9 refers to φ15.88. Pipes to be used are made of phosphorus deoxidized copper. - For example, when the
outdoor unit 10 has a cooling capacity of 2.2 kW, a pipe to be used as thegas pipe 30 most desirably has an outer diameter φ of 9.52 mm (φ is hereinafter omitted) (corresponding to "double circle"), more desirably 6.35 mm (corresponding to "circle"), desirably 12.7 mm (corresponding to "triangle"). A pipe having an outer diameter of 15.9 mm or more cannot be used. A pipe to be used as theliquid pipe 40 most desirably has an outer diameter of 6.35 mm (corresponding to "double circle"), more desirably 9.52 mm (corresponding to "circle"), desirably 12.7 mm (corresponding to "triangle"). Theoutdoor unit 10 having a cooling capacity of 2.5 kW has the same results as theoutdoor unit 10 having a cooling capacity of 2.2 kW. - When the
outdoor unit 10 has a cooling capacity in the range of 2.8 to 5.6 kW, a pipe to be used as thegas pipe 30 most desirably has an outer diameter of 9.52 mm (corresponding to "double circle"), second most desirably 6.35 or 12.7 mm (corresponding to "circle"), third most desirably 15.9 mm (corresponding to "triangle"). Theliquid pipe 40 has the same results as in the case of a cooling capacity of 2.2 or 2.5 kW. - When the
outdoor unit 10 has a cooling capacity of 6.3 kW, a pipe to be used as thegas pipe 30 most desirably has an outer diameter of 12.7 mm (corresponding to "double circle"), second most desirably 9.52 or 15.9 mm (corresponding to "circle"), third most desirably 6.53 mm (corresponding to "triangle"). Theliquid pipe 40 has the same results as in the case of a cooling capacity of 2.2 or 2.5 kW. - When the
outdoor unit 10 has a cooling capacity in the range of 7.1 to 9.5 kW, a pipe to be used as thegas pipe 30 most desirably has an outer diameter of 12.7 mm (corresponding to "double circle"), second most desirably 9.52 or 15.9 mm (corresponding to "circle"). Theliquid pipe 40 most desirably has an outer diameter of 9.52 mm (corresponding to "double circle"), second most desirably 6.35 or 12.7 mm (corresponding to "circle"). - As described above, the outer diameters of pipes to be desirably used as the
gas pipe 30 and theliquid pipe 40 increase with increasing cooling capacity.Fig. 4 shows the ratios (mm/kW) of the outer diameters of thegas pipe 30 and theliquid pipe 40 to cooling capacity. - The ratio (mm/kW) of the outer diameter of the
gas pipe 30 to cooling capacity desirably ranges from 1.00 to 5.77 (corresponding to "double circle", "circle", or "triangle"), more desirably 1.00 to 4.54 (corresponding to "double circle" or "circle"), most desirably 1.34 to 4.33 (corresponding to "double circle"). Thus, the outer diameter of thegas pipe 30 is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of theoutdoor unit 10 ranges from 0.67 to 5.77. - Likewise, the ratio (mm/kW) of the outer diameter of the
liquid pipe 40 to cooling capacity desirably ranges from 0.67 to 5.77 (corresponding to "double circle", "circle", or "triangle"), more desirably 0.67 to 4.33 (corresponding to "double circle" or "circle"), most desirably 1.00 to 2.89 (corresponding to "double circle"). Thus, the outer diameter of theliquid pipe 40 is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of theoutdoor unit 10 ranges from 1.00 to 5.77. - Thus, an HFC refrigerant, particularly HFO-1234yf in the case of HFO refrigerants or HFC32 in the case of HFC refrigerants, is mixed to suppress the decomposition reaction of HFO-1123. The optimum outer diameters of pipes to be used as the
gas pipe 30 and theliquid pipe 40 can be chosen on the assumption that the decomposition reaction of HFO-1123 is suppressed, and this can reduce the cost of theheat pump apparatus 100. - Although the
heat pump apparatus 100 described inEmbodiment 1 includes one indoor unit coupled to one outdoor unit, aheat pump apparatus 200 described in Embodiment 2 includes a plurality of indoor units coupled to one outdoor unit. - The
heat pump apparatus 200 includes threeindoor units outdoor unit 10A. - The
outdoor unit 10A includes no expansion valve, and theindoor units expansion valves - The gas pipes of the
heat pump apparatus 200 are composed of amain gas pipe 30a, agas pipe 31, agas pipe 32a, agas pipe 32b, and agas pipe 32c. - The liquid pipes of the
heat pump apparatus 200 are composed of a mainliquid pipe 40a, aliquid pipe 41, aliquid pipe 42a, aliquid pipe 42b, and aliquid pipe 42c. - The
main gas pipe 30a, thegas pipe 31, thegas pipe 32a, thegas pipe 32b, and thegas pipe 32c are coupled together with a branch joint 50a and a branch joint 50b. The mainliquid pipe 40a, theliquid pipe 41, theliquid pipe 42a, theliquid pipe 42b, and theliquid pipe 42c are coupled together with a branch joint 55a and a branch joint 55b. - The branch joint 50a, the branch joint 50b, the branch joint 55a, and the branch joint 55b are three-way branch joints each having opening ports in three directions.
- The three opening ports of the branch joint 50a are coupled to the
main gas pipe 30a, thegas pipe 31, and thegas pipe 32a. - The three opening ports of the branch joint 50b are coupled to the
gas pipe 31, thegas pipe 32c, and thegas pipe 32b. - The three opening ports of the branch joint 55a are coupled to the main
liquid pipe 40a, theliquid pipe 41, and theliquid pipe 42a. - The three opening ports of the branch joint 55b are coupled to the
liquid pipe 41, theliquid pipe 42c, and theliquid pipe 42b. - The
gas pipe 32a is coupled to a gas pipe joint 22a of theindoor unit 20A, thegas pipe 32b is coupled to the gas pipe joint 22b of theindoor unit 20B, and thegas pipe 32c is coupled to the gas pipe joint 22c of theindoor unit 20C. - The
liquid pipe 42a is coupled to the liquid pipe joint 23a of theindoor unit 20A, theliquid pipe 42b is coupled to the liquid pipe joint 23b of theindoor unit 20B, and theliquid pipe 42c is coupled to the liquid pipe joint 23c of theindoor unit 20C. - First, a refrigerant flow in heating operation will be described below. A high-temperature high-pressure gas refrigerant discharged from a
compressor 12a flows into a four-way valve 13a. The high-temperature high-pressure gas refrigerant flows from the four-way valve 13a to the gas pipe joint 16a, themain gas pipe 30a, and the branch joint 50a. The refrigerant is divided by the branch joint 50a into thegas pipe 32a and thegas pipe 31. The refrigerant flowing through thegas pipe 31 is divided by the branch joint 50b into thegas pipe 32b and thegas pipe 32c. The high-temperature high-pressure gas refrigerant flows through thegas pipes indoor heat exchangers indoor units indoor heat exchangers expansion valves - The low-temperature high-pressure two-phase gas-liquid refrigerant from the
expansion valve 24a flows through theliquid pipe 42a, the branch joint 55a, the mainliquid pipe 40a, and the liquid pipe joint 17a into anoutdoor heat exchanger 14a. - The low-temperature high-pressure two-phase gas-liquid refrigerant from the
expansion valve 24b flows through theliquid pipe 42b, the branch joint 55b, theliquid pipe 41, the branch joint 55a, the mainliquid pipe 40a, and the liquid pipe joint 17a into theoutdoor heat exchanger 14a. - The low-temperature high-pressure two-phase gas-liquid refrigerant from the
expansion valve 24c flows through theliquid pipe 42c, the branch joint 55b, theliquid pipe 41, the branch joint 55a, the mainliquid pipe 40a, and the liquid pipe joint 17a into theoutdoor heat exchanger 14a. - The low-temperature high-pressure two-phase gas-liquid refrigerant from the
expansion valves outdoor heat exchanger 14a and becomes a high-temperature low-pressure gas refrigerant. The high-temperature low-pressure gas refrigerant from theoutdoor heat exchanger 14a flows through the four-way valve 13a into anaccumulator 11 a. - Next, a refrigerant flow in cooling operation will be described below. A high-temperature high-pressure gas refrigerant discharged from the
compressor 12a flows through the four-way valve 13a into theoutdoor heat exchanger 14a. The high-temperature high-pressure gas refrigerant exchanges heat with outdoor air in theoutdoor heat exchanger 14a and becomes a low-temperature high-pressure liquid refrigerant. The low-temperature high-pressure liquid refrigerant from theoutdoor heat exchanger 14a flows through the liquid pipe joint 17a and the mainliquid pipe 40a into the branch joint 55a. The refrigerant is divided by the branch joint 55a into theliquid pipe 41 and theliquid pipe 42a. The refrigerant flowing through theliquid pipe 41 is divided by the branch joint 55b into theliquid pipe 42b and theliquid pipe 42c. The low-temperature high-pressure liquid refrigerant flows through theliquid pipe 42a, theliquid pipe 42b, and theliquid pipe 42c and the liquid pipe joint 23a, the liquid pipe joint 23b, and the liquid pipe joint 23c into theexpansion valve 24a, theexpansion valve 24b, and theexpansion valve 24c. The low-temperature high-pressure liquid refrigerant are depressurized by theexpansion valve 24a, theexpansion valve 24b, and theexpansion valve 24c and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant. The low-temperature low-pressure two-phase gas-liquid refrigerant from theexpansion valve 24a, theexpansion valve 24b, and theexpansion valve 24c flows into theindoor heat exchanger 21 a, theindoor heat exchanger 21 b, and theindoor heat exchanger 21 c, exchanges heat with indoor air, and becomes a high-temperature low-pressure gas refrigerant. - The high-temperature low-pressure gas refrigerant from the
indoor heat exchanger 21 a flows through the gas pipe joint 22a, thegas pipe 32a, the branch joint 50a, and themain gas pipe 30a. - The high-temperature low-pressure gas refrigerant from the
indoor heat exchanger 21 b flows through the gas pipe joint 22b, thegas pipe 32b, the branch joint 50b, thegas pipe 31, the branch joint 50a, and themain gas pipe 30a. - The high-temperature low-pressure gas refrigerant from the
indoor heat exchanger 21 c flows through the gas pipe joint 22c, thegas pipe 32c, thegas pipe 32c, the branch joint 50b, thegas pipe 31, the branch joint 50a, and themain gas pipe 30a. - The high-temperature low-pressure gas refrigerant flowing through the
main gas pipe 30a flows through the gas pipe joint 16a and the four-way valve 13a into theaccumulator 11 a. - In heating operation, a high-temperature high-pressure gas refrigerant flows through the
main gas pipe 30a, and in cooling operation, a high-temperature low-pressure gas refrigerant flows through themain gas pipe 30a. - In heating operation, a low-temperature high-pressure two-phase gas-liquid refrigerant flows through the main
liquid pipe 40a, and in cooling operation, low-temperature high-pressure liquid refrigerant flows through the mainliquid pipe 40a. - In Embodiment 2, the outer diameter and thickness of the
main gas pipe 30a and the mainliquid pipe 40a satisfy the following conditions. - Outer diameter φ (mm) of
main gas pipe 30a > Outer diameter φ (mm) ofgas pipe 31 - Outer diameter φ (mm) of main
liquid pipe 40a > Outer diameter φ (mm) ofliquid pipe 41 - Thickness (mm) of
main gas pipe 30a > Thickness (mm) ofgas pipe 31 - Thickness (mm) of main
liquid pipe 40a > Thickness (mm) ofliquid pipe 41 - The amount of refrigerant flowing through the
main gas pipe 30a into thegas pipe 31 is decreased by the amount of refrigerant flowing through thebranch joints indoor unit 20A. Thus, thegas pipe 31 can have a smaller outer diameter and thickness than themain gas pipe 30a. Likewise, the amount of refrigerant flowing through the mainliquid pipe 40a into theliquid pipe 41 is decreased by the amount of refrigerant flowing into theindoor unit 20A. Thus, theliquid pipe 41 can have a smaller outer diameter and thickness than the mainliquid pipe 40a. -
Fig. 6 shows the outer diameters φ (mm) of themain gas pipe 30a and the mainliquid pipe 40a usable depending on the cooling capacity of theoutdoor unit 10A according to Embodiment 2. LikeFig. 4 ,Fig. 7 shows the ratio (mm/kW) of the outer diameter of themain gas pipe 30a or the mainliquid pipe 40a to the cooling capacity of theoutdoor unit 10A. - When a plurality of
indoor units outdoor unit 10A as in theheat pump apparatus 200, theoutdoor unit 10A often has a cooling capacity of more than 10 kW. In Embodiment 2, the outer diameters of themain gas pipe 30a and the mainliquid pipe 40a to be chosen in consideration of the design pressure of theheat pump apparatus 200 that includes theoutdoor unit 10A having a cooling capacity of 10 kW or more and less than 40 kW will be described below with reference toFigs. 6 and7 . - When the
outdoor unit 10A has a cooling capacity of 10 kW or more and less than 20 kW, themain gas pipe 30a most desirably has an outer diameter of 19.1, 22.2, or 25.4 mm (corresponding to "double circle"), more desirably 15.9, 28.6, or 31.8 mm (corresponding to "circle"), desirably 34.9 mm (corresponding to "triangle"). - When the
outdoor unit 10A has a cooling capacity of 20 kW or more and less than 30 kW, themain gas pipe 30a most desirably has an outer diameter of 22.2, 25.4, or 28.6 mm (corresponding to "double circle"), more desirably 15.9, 19.1, 31.8, or 34.9 mm (corresponding to "circle"). - When the
outdoor unit 10A has a cooling capacity of 30 kW or more and less than 40 kW, themain gas pipe 30a most desirably has an outer diameter of 25.4, 28.6, or 31.8 mm (corresponding to "double circle"), more desirably 19.1, 22.2, or 34.9 mm (corresponding to "circle"), desirably 15.9 mm (corresponding to "triangle"). - When the
outdoor unit 10A has a cooling capacity of 10 kW or more and less than 20 kW, the mainliquid pipe 40a most desirably has an outer diameter of 9.52 or 12.7 mm (corresponding to "double circle"), more desirably 6.35 or 15.9 mm (corresponding to "circle"), desirably 19.1 mm (corresponding to "triangle"). - When the
outdoor unit 10A has a cooling capacity of 20 kW or more and less than 30 kW, the mainliquid pipe 40a most desirably has an outer diameter of 12.7 mm (corresponding to "double circle"), more desirably 6.35, 9.52, 15.9, or 19.1 mm (corresponding to "circle"). - When the
outdoor unit 10A has a cooling capacity of 30 kW or more and less than 40 kW, the mainliquid pipe 40a most desirably has an outer diameter of 12.7 or 15.9 mm (corresponding to "double circle"), more desirably 9.52 or 19.1 mm (corresponding to "circle"), desirably 6.35 mm (corresponding to "triangle"). - The outer diameters of pipes to be desirably used as the
main gas pipe 30a and the mainliquid pipe 40a increase with increasing cooling capacity.Fig. 7 shows the ratios (mm/kW) of the outer diameters of themain gas pipe 40a and the mainliquid pipe 40a to cooling capacity. - The ratio (mm/kW) of the outer diameter of the
main gas pipe 30a to cooling capacity desirably ranges from 0.40 to 3.49 (corresponding to "double circle", "circle", or "triangle"), more desirably 0.48 to 3.18 (corresponding to "double circle" or "circle"), most desirably 0.64 to 2.54 (corresponding to "double circle"). Thus, the outer diameter of themain gas pipe 30a is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of theoutdoor unit 10 ranges from 0.40 to 3.49. - Likewise, the ratio (mm/kW) of the outer diameter of the main
liquid pipe 40a to cooling capacity desirably ranges from 0.16 to 1.91 (corresponding to "double circle", "circle", or "triangle"), more desirably 0.24 to 1.59 (corresponding to "double circle" or "circle"), most desirably 0.32 to 1.27 (corresponding to "double circle"). Thus, the outer diameter of the mainliquid pipe 40a is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of theoutdoor unit 10 ranges from 0.16 to 1.91. - Thus, an HFC refrigerant, particularly HFO-1234yf in the case of HFO refrigerants or HFC32 in the case of HFC refrigerants, is mixed to suppress the decomposition reaction of HFO-1123. The optimum outer diameters of pipes to be used as the
main gas pipe 30a and the mainliquid pipe 40a can be chosen on the assumption that the decomposition reaction of HFO-1123 is suppressed, and this can reduce the cost of theheat pump apparatus 200. - Although the
heat pump apparatus 200 described in Embodiment 2 includes a plurality of indoor units coupled to one outdoor unit, aheat pump apparatus 300 described in Embodiment 3 includes a plurality of indoor units coupled to two outdoor units. - The
heat pump apparatus 300 includes threeindoor units outdoor units outdoor units indoor units expansion valves - The gas pipes of the
heat pump apparatus 300 are composed of agas pipe 33a, agas pipe 33b, amain gas pipe 30b, agas pipe 31, agas pipe 32a, and agas pipe 32c. - The liquid pipes of the
heat pump apparatus 300 are composed of aliquid pipe 43a, aliquid pipe 43b, a mainliquid pipe 40b, aliquid pipe 41, aliquid pipe 42a, aliquid pipe 42b, and aliquid pipe 42c. - The
gas pipe 33a, thegas pipe 33b, themain gas pipe 30b, thegas pipe 31, thegas pipe 32a, and thegas pipe 32c are coupled together with a branch joint 60, a branch joint 50a, and a branch joint 50b. - The
liquid pipe 43a, theliquid pipe 43b, the mainliquid pipe 40b, theliquid pipe 41, theliquid pipe 42a, theliquid pipe 42b, and theliquid pipe 42c are coupled together with a branch joint 65, a branch joint 55a, and a branch joint 55b. - Like the branch joint 50b, the branch joint 55a, and the branch joint 55b, the branch joint 60 and the branch joint 65 are three-way branch joints each having opening ports in three directions.
- The three opening ports of the branch joint 50a are coupled to the
main gas pipe 30b, thegas pipe 31, and thegas pipe 32a. - The three opening ports of the branch joint 50b are coupled to the
gas pipe 31, thegas pipe 32c, and thegas pipe 32b. - The three opening ports of the branch joint 55a are coupled to the main
liquid pipe 40b, theliquid pipe 41, and theliquid pipe 42a. - The three opening ports of the branch joint 55b are coupled to the
liquid pipe 41, theliquid pipe 42c, and theliquid pipe 42b. - The three opening ports of the branch joint 60 are coupled to the
main gas pipe 30b, thegas pipe 33a, and thegas pipe 33b. - The three opening ports of the branch joint 65 are coupled to the main
liquid pipe 40b, theliquid pipe 43a, and theliquid pipe 43b. - The
gas pipe 32a is coupled to a gas pipe joint 22a of theindoor unit 20A, thegas pipe 32b is coupled to the gas pipe joint 22b of theindoor unit 20B, and thegas pipe 32c is coupled to the gas pipe joint 22c of theindoor unit 20C. - The
liquid pipe 42a is coupled to the liquid pipe joint 23a of theindoor unit 20A, theliquid pipe 42b is coupled to the liquid pipe joint 23b of theindoor unit 20B, and theliquid pipe 42c is coupled to the liquid pipe joint 23c of theindoor unit 20C. - First, a refrigerant flow in heating operation will be described below. A high-temperature high-pressure gas refrigerant discharged from the
compressor 12a of theoutdoor unit 10A flows into a four-way valve 13a. The high-temperature high-pressure gas refrigerant flows from the four-way valve 13a to the gas pipe joint 16a, thegas pipe 33a, the branch joint 60, themain gas pipe 30b, and the branch joint 50a. The refrigerant is divided by the branch joint 50a into thegas pipe 32a and thegas pipe 31. The refrigerant flowing through thegas pipe 31 is divided by the branch joint 50b into thegas pipe 32b and thegas pipe 32c. The high-temperature high-pressure gas refrigerant flows through thegas pipes indoor heat exchangers indoor units indoor heat exchangers expansion valves - A high-temperature high-pressure gas refrigerant discharged from the
compressor 12b of theoutdoor unit 10B flows through the gas pipe joint 16b and thegas pipe 33b and joins the refrigerant flowing from theoutdoor unit 10A at thebranch joint 60. - The low-temperature high-pressure two-phase gas-liquid refrigerant from the
expansion valve 24a flows through theliquid pipe 42a, the branch joint 55a, the mainliquid pipe 40b, the branch joint 65, theliquid pipe 43a, and the liquid pipe joint 17a into anoutdoor heat exchanger 14a. A refrigerant branched off at the branch joint 65 flows through theliquid pipe 43b and the liquid pipe joint 17b into anoutdoor heat exchanger 14b. - The low-temperature high-pressure two-phase gas-liquid refrigerant from the
expansion valve 24b flows through theliquid pipe 42b, the branch joint 55b, theliquid pipe 41, the branch joint 55a, the mainliquid pipe 40b, the branch joint 65, theliquid pipe 43a, and the liquid pipe joint 17a into theoutdoor heat exchanger 14a. A refrigerant branched off at the branch joint 65 flows through theliquid pipe 43b and the liquid pipe joint 17b into theoutdoor heat exchanger 14b. - The low-temperature high-pressure two-phase gas-liquid refrigerant from the
expansion valve 24c flows through theliquid pipe 42c, the branch joint 55b, theliquid pipe 41, the branch joint 55a, the mainliquid pipe 40b, the branch joint 65, theliquid pipe 43a, and the liquid pipe joint 17a into theoutdoor heat exchanger 14a. A refrigerant branched off at the branch joint 65 flows through theliquid pipe 43b and the liquid pipe joint 17b into anoutdoor heat exchanger 14b. - The low-temperature high-pressure two-phase gas-liquid refrigerant exchanges heat with outdoor air in the
outdoor heat exchanger 14a and becomes a high-temperature low-pressure gas refrigerant. The high-temperature low-pressure gas refrigerant from theoutdoor heat exchanger 14a flows through the four-way valve 13a into anaccumulator 11 a. The low-temperature high-pressure two-phase gas-liquid refrigerant exchanges heat with outdoor air in theoutdoor heat exchanger 14b and becomes a high-temperature low-pressure gas refrigerant. The high-temperature low-pressure gas refrigerant from theoutdoor heat exchanger 14b flows through the four-way valve 13b into anaccumulator 11 b. - Next, a refrigerant flow in cooling operation will be described below. A high-temperature high-pressure gas refrigerant discharged from the
compressor 12a of theoutdoor unit 10A flows through the four-way valve 13a into theoutdoor heat exchanger 14a. The high-temperature high-pressure gas refrigerant exchanges heat with outdoor air in theoutdoor heat exchanger 14a and becomes a low-temperature high-pressure liquid refrigerant. The low-temperature high-pressure liquid refrigerant from theoutdoor heat exchanger 14a flows through the liquid pipe joint 17a, theliquid pipe 43a, the branch joint 65, and the mainliquid pipe 40b into the branch joint 55a. The refrigerant is divided by the branch joint 55a into theliquid pipe 41 and theliquid pipe 42a. The refrigerant flowing through theliquid pipe 41 is divided by the branch joint 55b into theliquid pipe 42b and theliquid pipe 42c. The low-temperature high-pressure liquid refrigerant flows through theliquid pipe 42a, theliquid pipe 42b, and theliquid pipe 42c and the liquid pipe joint 23a, the liquid pipe joint 23b, and the liquid pipe joint 23c into theexpansion valve 24a, theexpansion valve 24b, and theexpansion valve 24c. The low-temperature high-pressure liquid refrigerant are depressurized by theexpansion valve 24a, theexpansion valve 24b, and theexpansion valve 24c and becomes a low-temperature low-pressure two-phase gas-liquid refrigerant. The low-temperature low-pressure two-phase gas-liquid refrigerant from theexpansion valve 24a, theexpansion valve 24b, and theexpansion valve 24c flows into theindoor heat exchanger 21 a, theindoor heat exchanger 21 b, and theindoor heat exchanger 21 c, exchanges heat with indoor air, and becomes a high-temperature low-pressure gas refrigerant. - A high-temperature high-pressure gas refrigerant discharged from the
compressor 12b of theoutdoor unit 10B flows through the four-way valve 13b into theoutdoor heat exchanger 14b. The high-temperature high-pressure gas refrigerant exchanges heat with outdoor air in theoutdoor heat exchanger 14b and becomes a low-temperature high-pressure liquid refrigerant. The low-temperature high-pressure liquid refrigerant from theoutdoor heat exchanger 14b flows through the liquid pipe joint 17b and theliquid pipe 43b and joins the refrigerant flowing from theoutdoor unit 10A at thebranch joint 65. - The high-temperature low-pressure gas refrigerant from the
indoor heat exchanger 21 a flows through the gas pipe joint 22a, thegas pipe 32a, the branch joint 50a, themain gas pipe 30b, and thebranch joint 60. - The high-temperature low-pressure gas refrigerant from the
indoor heat exchanger 21 b flows through the gas pipe joint 22b, thegas pipe 32b, the branch joint 50b, thegas pipe 31, the branch joint 50a, themain gas pipe 30b, and thebranch joint 60. - The high-temperature low-pressure gas refrigerant from the
indoor heat exchanger 21 c flows through the gas pipe joint 22c, thegas pipe 32c, thegas pipe 32c, the branch joint 50b, thegas pipe 31, the branch joint 50a, themain gas pipe 30b, and thebranch joint 60. - The high-temperature low-pressure gas refrigerant is divided by the branch joint 60 into the
gas pipe 33a and thegas pipe 33b. - The high-temperature low-pressure gas refrigerant flowing through the
gas pipe 33a flows through the gas pipe joint 16a and the four-way valve 13a into theaccumulator 11 a. - The high-temperature low-pressure gas refrigerant flowing through the
gas pipe 33b flows through the gas pipe joint 16b and the four-way valve 13b into theaccumulator 11 b. - In heating operation, a high-temperature high-pressure gas refrigerant flows through the
main gas pipe 30b, and in cooling operation, a high-temperature low-pressure gas refrigerant flows through themain gas pipe 30b. - In heating operation, a low-temperature high-pressure two-phase gas-liquid refrigerant flows through the main
liquid pipe 40b, and in cooling operation, low-temperature high-pressure liquid refrigerant flows through the mainliquid pipe 40b. - In Embodiment 3, the outer diameter and thickness of the
gas pipe 30b and theliquid pipe 40b satisfy the following conditions. - Outer diameter φ (mm) of
main gas pipe 30b > Outer diameter φ (mm) ofgas pipe 31 - Outer diameter φ (mm) of
main gas pipe 30b > Outer diameter φ (mm) ofgas pipe 33a - Outer diameter φ (mm) of
main gas pipe 30b > Outer diameter φ (mm) ofgas pipe 33b - Thickness (mm) of
main gas pipe 30b > Thickness (mm) ofgas pipe 31 - Thickness (mm) of
main gas pipe 30b > Thickness (mm) ofgas pipe 33a - Thickness (mm) of
main gas pipe 30b > Thickness (mm) ofgas pipe 33b - Outer diameter φ (mm) of main
liquid pipe 40b > Outer diameter φ (mm) ofliquid pipe 41 - Outer diameter φ (mm) of main
liquid pipe 40b > Outer diameter φ (mm) ofliquid pipe 43a - Outer diameter φ (mm) of main
liquid pipe 40b > Outer diameter φ (mm) ofliquid pipe 43b - Thickness (mm) of main
liquid pipe 40b > Thickness (mm) ofliquid pipe 41 - Thickness (mm) of main
liquid pipe 40b > Thickness (mm) ofliquid pipe 43a - Thickness (mm) of main
liquid pipe 40b > Thickness (mm) ofliquid pipe 43b - The amount of refrigerant flowing through the
main gas pipe 30a into thegas pipe 31 is decreased by the amount of refrigerant flowing through thebranch joints indoor unit 20A. Thus, thegas pipe 31 can have a smaller outer diameter and thickness than themain gas pipe 30a. Refrigerant from theoutdoor unit 10A and refrigerant from theoutdoor unit 10B come together at the branch joints 60 and 65, thus increasing the refrigerant flow rate in themain gas pipe 30b and the mainliquid pipe 40b. Themain gas pipe 30b and the mainliquid pipe 40b must therefore have a larger outer diameter and thickness than thegas pipes liquid pipes -
Fig. 9 shows the outer diameters φ (mm) of themain gas pipe 30b and the mainliquid pipe 40b usable depending on the cooling capacities of theoutdoor unit 10A and theoutdoor unit 10B according to Embodiment 3. LikeFigs. 4 and7 ,Fig. 10 shows the ratios (mm/kW) of the outer diameters of themain gas pipe 30b and the mainliquid pipe 40b to the total cooling capacity of theoutdoor unit 10A and theoutdoor unit 10B. - When the
indoor units outdoor unit 10A has low cooling capacity, theoutdoor unit 10B as well as theoutdoor unit 10A is coupled to theindoor units heat pump apparatus 300, the design pressure depends on the total cooling capacity of theoutdoor unit 10A and theoutdoor unit 10B. Thus, the outer diameter and thickness of themain gas pipe 30b and the mainliquid pipe 40b can be chosen on the basis of the total cooling capacity of theoutdoor unit 10A and theoutdoor unit 10B. - For example, the total cooling capacity of the
outdoor unit 10A having a cooling capacity of 20 kW and theoutdoor unit 10B having a cooling capacity of 30 kW is 50 kW. - When the total cooling capacity of the
outdoor units - When the total cooling capacity of the
outdoor units - When the total cooling capacity of the
outdoor units - When the total cooling capacity of the
outdoor units - When the total cooling capacity of the
outdoor units - When the total cooling capacity of the
outdoor units - The outer diameters of pipes to be desirably used as the
main gas pipe 30b and the mainliquid pipe 40b increase with increasing cooling capacity.Fig. 10 shows the ratios (mm/kW) of the outer diameters of themain gas pipe 40a and the mainliquid pipe 40a to cooling capacity. - The ratio (mm/kW) of the outer diameter of the
main gas pipe 30b to cooling capacity desirably ranges from 0.32 to 1.11 (corresponding to "double circle", "circle", or "triangle"), more desirably 0.36 to 1.03 (corresponding to "double circle" or "circle"), most desirably 0.41 to 1.03 (corresponding to "double circle"). Thus, the outer diameter of themain gas pipe 30b is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of theoutdoor unit 10 ranges from 0.32 to 1.11. - Likewise, the ratio (mm/kW) of the outer diameter of the main
liquid pipe 40b to cooling capacity desirably ranges from 0.14 to 0.56 (corresponding to "double circle", "circle", or "triangle"), more desirably 0.16 to 0.48 (corresponding to "double circle" or "circle"), most desirably 0.23 to 0.40 (corresponding to "double circle"). Thus, the outer diameter of the mainliquid pipe 40a is chosen such that the ratio (mm/kW) of the outer diameter to the cooling capacity of theoutdoor unit 10 ranges from 0.14 to 1.56. - Although the
heat pump apparatus 300 described in Embodiment 3 includes threeindoor units outdoor units gas pipe 32c and theliquid pipe 42c is provided with an additional branch joint, and the branch joint is coupled to a gas pipe and a liquid pipe. The gas pipe and liquid pipe are coupled to an indoor unit. In this manner, an indoor unit can be added by retrofitting a gas pipe and a liquid pipe with a branch joint. - When four or more indoor units are installed, two outdoor units may have insufficient cooling capacity. In such a case, an outdoor unit may be added. For example, when three outdoor units are used, each of the
main gas pipe 30b and the mainliquid pipe 40b is provided with an additional branch joint, and the branch joint is coupled to a gas pipe and a liquid pipe. The gas pipe and liquid pipe are coupled to an indoor unit. -
Fig. 11 shows the outer diameters φ (mm) of a main gas pipe and a main liquid pipe in the case that a plurality of outdoor units have a total cooling capacity of 70 kW or more.Fig. 12 shows the ratios (mm/kW) of the outer diameters of a main gas pipe and a main liquid pipe to the total cooling capacity of a plurality of outdoor units. For example, the total cooling capacity of three outdoor units each having a cooling capacity of 30 kW is 90 kW. - When the total cooling capacity of a plurality of outdoor units is 70 kW or more and less than 80 kW, 31.8, 34.9, 38.1, and 41.3 mm are most desirable (corresponding to "double circle"), 25.4, 28.6, and 44.5 mm are more desirable (corresponding to "circle"), and 50.8 mm is desirable (corresponding to "triangle").
- When the total cooling capacity of a plurality of outdoor units is 80 kW or more and less than 90 kW, 38.1, 41.3, and 44.5 mm are most desirable (corresponding to "double circle"), and 25.4, 28.6, 31.8, 34.9, and 50.8 mm are more desirable (corresponding to "circle").
- When the total cooling capacity of a plurality of outdoor units is 90 kW or more and less than 100 kW, 38.1, 41.3, and 44.5 mm are most desirable (corresponding to "double circle"), 28.6, 31.8, 34.9, and 50.8 mm are more desirable (corresponding to "circle"), and 25.4 mm is desirable (corresponding to "triangle").
- When the total cooling capacity of a plurality of outdoor units is 70 kW or more and less than 80 kW, 15.9 and 19.1 mm are most desirable (corresponding to "double circle"), 12.7 and 22.2 mm are more desirable (corresponding to "circle"), and 25.4 mm is desirable (corresponding to "triangle").
- When the total cooling capacity of a plurality of outdoor units is 80 kW or more and less than 90 kW, 19.1 and 22.2 mm are most desirable (corresponding to "double circle"), 12.7, 15.9, and 25.4 mm are more desirable (corresponding to "circle"), and 28.6 mm is desirable (corresponding to "triangle").
- When the total cooling capacity of a plurality of outdoor units is 90 kW or more and less than 100 kW, 19.1 and 22.2 mm are most desirable (corresponding to "double circle"), 15.9 and 25.4 mm are more desirable (corresponding to "circle"), and 12.7 and 28.6 mm are desirable (corresponding to "triangle").
- The outer diameters of pipes to be desirably used as a main gas pipe and a main liquid pipe increase with increasing cooling capacity.
Fig. 12 shows the ratios (mm/kW) of the outer diameters of a main gas pipe and a main liquid pipe to cooling capacity. - When the total cooling capacity of a plurality of outdoor units is 70 kW or more and less than 100 kW, the ratio (mm/kW) of the outer diameter of the main gas pipe to cooling capacity desirably ranges from 0.25 to 0.73 (corresponding to "double circle", "circle", or "triangle"), more desirably 0.28 to 0.64 (corresponding to "double circle" or "circle"), most desirably 0.38 to 0.59 (corresponding to "double circle"). Thus, the outer diameter of a main gas pipe is chosen such that the ratio (mm/kW) of the outer diameter to the total cooling capacity of outdoor units ranges from 0.25 to 0.73.
- Likewise, the ratio (mm/kW) of the outer diameter of a main liquid pipe to cooling capacity desirably ranges from 0.13 to 0.36 (corresponding to "double circle", "circle", or "triangle"), more desirably 0.14 to 0.32 (corresponding to "double circle" or "circle"), most desirably 0.19 to 0.28 (corresponding to "double circle"). Thus, the outer diameter of a main liquid pipe is chosen such that the ratio (mm/kW) of the outer diameter to the total cooling capacity of outdoor units ranges from 0.13 to 0.36.
- Thus, an HFC refrigerant, particularly HFO-1234yf in the case of HFO refrigerants or HFC32 in the case of HFC refrigerants, is mixed to suppress the decomposition reaction of HFO-1123. The optimum outer diameters of pipes to be used as the
main gas pipe 30b and the mainliquid pipe 40b can be chosen on the assumption that the decomposition reaction of HFO-1123 is suppressed, and this can reduce the cost of theheat pump apparatus 300. - The thickness of pipes used in the present invention (
Embodiments 1 to 3) will be described below. - It is desirable that a pipe having an outer diameter in the range of 6.35 to 12.7 mm be made of an O-material having a thickness of 0.8 mm or more.
- A pipe having an outer diameter of 15.9 mm is preferably made of an O-material having a thickness of 1.0 mm or more.
- It is desirable that a pipe having an outer diameter in the range of 19.1 to 28.6 mm be made of a 1/2H-material having a thickness of 1.0 mm or more.
- It is desirable that a pipe having an outer diameter of 31.8 mm be made of a 1/2H-material having a thickness of 1.1 mm or more.
- It is desirable that a pipe having an outer diameter of 34.9 mm be made of a 1/2H-material having a thickness of 1.2 mm or more.
- It is desirable that a pipe having an outer diameter of 38.1 mm be made of a 1/2H-material having a thickness of 1.35 mm or more.
- It is desirable that a pipe having an outer diameter of 41.3 mm be made of a 1/2H-material having a thickness of 1.45 mm or more.
- It is desirable that a pipe having an outer diameter of 44.5 mm be made of a 1/2H-material having a thickness of 1.55 mm or more.
- It is desirable that a pipe having an outer diameter in the range of 50.8 to 54.0 mm be made of a 1/2H-material having a thickness of 1.80 mm or more.
- O-materials are "materials in the softest state after annealing", and 1/2H-materials are "materials work hardened by cold working".
- The upper limit of the thickness is 1.3 times the lower limit of the thickness. For example, for a pipe having an outer diameter of 6.35 mm, the lower limit of the thickness is 0.8 mm, and the upper limit of the thickness is 1.04 mm (0.8 mm x 1.3). Thus, the thickness of a pipe having an outer diameter of 6.35 mm ranges from 0.8 to 10.4 mm.
- If pipes widely used with R410A have a thickness chosen as described above for their outer diameters, the pipes can be applied to heat pump apparatus in which HFO-1123 and an HFC refrigerant circulate. This obviates the need to produce a special pipe having a large thickness designed for HFO-1123. Thus, a heat pump apparatus can be produced without increased pipe costs.
- The term "gas pipe", as used herein, refers to a pipe through which a high-temperature high-pressure gas refrigerant discharged from a compressor flows before entering a condenser. The term "liquid pipe", as used herein, refers to a pipe through which a low-temperature high-pressure liquid refrigerant from an evaporator or a low-temperature low-pressure two-phase gas-liquid refrigerant passing through an expansion valve flows.
- The terms "main gas pipe" and "main gas pipe" in Embodiments 2 and 3 refer to a gas pipe and a liquid pipe having the largest outer diameter out of a plurality of gas pipes coupled with a branch joint.
- For a heat pump apparatus including a plurality of outdoor units, the outer diameter of a pipe coupled to a branch joint at which refrigerant from an outdoor unit or indoor unit joins is larger than the outer diameters of pipes coupled to a gas pipe joint and a liquid pipe joint of a particular outdoor unit. Thus, in a heat pump apparatus including a plurality of outdoor units, a pipe having the largest outer diameter is referred to as a main pipe.
- In the
heat pump apparatus Embodiments 1 to 3), an outdoor unit and an indoor unit are coupled together with a gas pipe and a liquid pipe, and refrigerant flows into an indoor unit. However, a heat pump apparatus may include an intermediate device in which an outdoor unit is coupled to an intermediate unit, and the intermediate unit is coupled to an indoor unit. - The intermediate device includes an intermediate heat exchanger, and refrigerant from an outdoor unit exchanges heat with a heat medium, such as water or brine, in the intermediate heat exchanger. After heat exchange with the refrigerant, the heat medium flows into an indoor unit. The refrigerant does not flow into the indoor unit. In such a heat pump apparatus including an intermediate device, a gas pipe and a liquid pipe refers to pipes between an outdoor unit and the intermediate device.
- The phrase "a heat pump apparatus in which refrigerant circulates between an indoor unit and an outdoor unit", as used herein, includes "a heat pump apparatus equipped with an intermediate unit in which refrigerant circulates between the intermediate unit and an outdoor unit", including a heat pump apparatus in which a heat medium, such as water or brine, rather than refrigerant, flows into an indoor unit.
- Specific examples of ester lubricating oil and ether lubricating oil will be described below.
- Examples of the ester lubricating oil include dibasic acid ester oil, polyol ester oil, complex ester oil, and polyol carbonate oil.
- The dibasic acid ester oil is preferably an ester between a dibasic acid having 5 to 10 carbon atoms (glutaric acid, adipic acid, pimelic acid, suberic acid, azelaic acid, or sebacic acid) and a monohydric alcohol having a linear or branched alkyl group and having 1 to 15 carbon atoms (methanol, ethanol, propanol, butanol, pentanol, hexanol, heptanol, octanol, nonanol, decanol, undecanol, dodecanol, tridecanol, tetradecanol, or pentadecanol). More specifically, the dibasic acid ester oil is ditridecyl glutarate, di(2-ethylhexyl) adipate, diisodecyl adipate, ditridecyl adipate, or di(3-ethylhexyl) sebacate.
- The polyol ester oil is preferably an ester between a diol (ethylene glycol, 1,3-propanediol, propylene glycol, 1,4-butanediol, 1,2-butanediol, 1,5-pentadiol, neopentyl glycol, 1,7-heptanediol, or 1,12-dodecanediol) or a polyol having 3 to 20 hydroxy groups (trimethylolethane, trimethylolpropane, trimethylolbutane, pentaerythritol, glycerin, sorbitol, sorbitan, or a sorbitol glycerin condensate) and a fatty acid having 6 to 20 carbon atoms (a linear or branched fatty acid, such as hexanoic acid, heptanoic acid, octanoic acid, nonanoic acid, decanoic acid, undecanoic acid, dodecanoic acid, eicosanoic acid, or oleic acid, or a so-called neo acid having a quaternary α carbon atom).
- The polyol ester oil may have a free hydroxy group.
- The polyol ester oil is preferably an ester (trimethylolpropane tripelargonate, pentaerythritol 2-ethylhexanoate, or pentaerythritol tetrapelargonate) of a hindered alcohol (neopentyl glycol, trimethylolethane, trimethylolpropane, trimethylolbutane, or pentaerythritol).
- The complex ester oil refers to an ester between a fatty acid and a dibasic acid and a monohydric alcohol and a polyol. The fatty acid, dibasic acid, monohydric alcohol, and polyol may be those described above.
- The polyol carbonate oil refers to an ester between carbonic acid and a polyol.
- The polyol may be a diol or polyol described above. The polyol carbonate oil may be a product of ring-opening polymerization of a cyclic alkylene carbonate.
- The ether lubricating oil may be a poly(vinyl ether) oil or a polyoxyalkylene lubricating oil.
- The poly(vinyl ether) oil may be a polymerization product of a vinyl ether monomer, such as an alkyl vinyl ether, or a copolymer of a vinyl ether monomer and a hydrocarbon monomer having an olefinic double bond.
- These vinyl ether monomers may be used alone or in combination.
- Examples of the hydrocarbon monomer having an olefinic double bond include ethylene, propylene, butenes, pentenes, hexenes, heptenes, octenes, diisobutylene, triisobutylene, styrene, α-methylstyrene, and alkyl substituted styrenes. These hydrocarbon monomers having an olefinic double bond may be used alone or in combination.
- The poly(vinyl ether) copolymer may be a block or random copolymer.
- These poly(vinyl ether)s may be used alone or in combination.
- The present invention can be utilized in air-conditioning apparatus and freezing devices that utilize a heat pump cycle.
-
- 10
outdoor unit 20indoor unit 30gas pipe 30amain gas pipe 30bmain gas pipe 40liquid pipe 40a mainliquid pipe 40b main liquid pipe
Claims (6)
- A heat pump apparatus comprising:an indoor unit;an outdoor unit having a cooling capacity (kW) in the range of 2.2 to 9.5 kW;a refrigerant circulating between the indoor unit and the outdoor unit, the refrigerant being a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123;a gas pipe communicating between the indoor unit and the outdoor unit; anda liquid pipe communicating between the indoor unit and the outdoor unit,the gas pipe and the outdoor unit being configured to satisfy the following formula (1), and the liquid pipe and the outdoor unit being configured to satisfy the following formula (2):(1) 1.00 ≤ an outer diameter φ (mm) of the gas pipe/the cooling capacity (kW) of the outdoor unit ≤ 5.77(2) 0.67 ≤ an outer diameter φ (mm) of the liquid pipe/the cooling capacity (kW) the of outdoor unit ≤ 5.77
- A heat pump apparatus comprising:a plurality of indoor units;at least one outdoor unit having a cooling capacity (kW) of 10 kW or more and less than 40 kW;a refrigerant circulating between the plurality of indoor units and the at least one outdoor unit, the refrigerant being a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123;a main gas pipe communicating between the plurality of indoor units and the at least one outdoor unit; anda main liquid pipe communicating between the plurality of indoor units and the at least one outdoor unit,the main gas pipe and the at least one outdoor unit being configured to satisfy the following formula (1), and the liquid pipe and the at least one outdoor unit being configured to satisfy the following formula (2):(1) 0.40 ≤ an outer diameter φ (mm) of the main gas pipe/the cooling capacity (kW) of the at least one outdoor unit ≤ 3.49(2) 0.16 ≤ an outer diameter φ (mm) of the main liquid pipe/the cooling capacity (kW) of the at least one outdoor unit ≤ 1.91
- A heat pump apparatus comprising:a plurality of indoor units;at least two outdoor units, the at least two outdoor units having a total cooling capacity (kW) of 40 kW or more and less than 70 kW;a refrigerant circulating between the plurality of indoor units and the at least two outdoor units, the refrigerant being a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123;a main gas pipe communicating between the plurality of indoor units and the at least two outdoor units; anda main liquid pipe comunicating between the plurality of indoor units and the at least two outdoor units,the main gas pipe and the at least two outdoor units being configured to satisfy the folloinwg formula (1), and the main liquid pipe and the at least two outdoor units being confiugred to satisfy the following formula (2):(1) 0.32 ≤ an outer diameter φ (mm) of the main gas pipe/ the total cooling capacity (kW) of the at least two outdoor units ≤ 1.11(2) 0.14 ≤ an outer diameter φ (mm) of the main liquid pipe/the total cooling capacity (kW) of the at least two outdoor units ≤ 0.56
- A heat pump apparatus comprising:a plurality of indoor units;at least three outdoor units having a total cooling capacity (kW) of 70 kW or more and less than 100 kW;a refrigerant circulating between the plurality of indoor units and the at least three outdoor units, the refrigerant being a mixed refrigerant of HFO-1123 and an HFC refrigerant other than HFO-1123;a main gas pipe communicating between the plurality of indoor units and the at least three outdoor units; anda liquid pipe communicating between the plurality of indoor units and the at least three outdoor units,the main gas pipe and the at least three outdoor units being configured to satisfy the following formula (1), and the liquid pipe and the at least three outdoor units being confiugured to satisfy the following formula (2):(1) 0.25 ≤ an outer diameter φ (mm) of the main gas pipe /the total cooling capacity (kW) of the plurality of indoor units ≤ 0.73(2) 0.13 ≤ an outer diameter φ (mm) of the liquid pipe /the total cooling capacity (kW) of the plurality of indoor units ≤ 0.36
- The heat pump apparatus of any one of Claims 1 to 4, wherein the refrigerant is a mixed refrigerant of HFO-1123 and HFO1234yf or a mixed refrigerant of HFO-1123 and HFO32.
- The heat pump apparatus of Claim 5, wherein the refrigerant is a mixed refrigerant of HFO-1123 and HFO32.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2014/001483 WO2015140827A1 (en) | 2014-03-17 | 2014-03-17 | Heat pump device |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3128259A1 true EP3128259A1 (en) | 2017-02-08 |
Family
ID=54143857
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14886307.9A Withdrawn EP3128259A1 (en) | 2014-03-17 | 2014-03-17 | Heat pump device |
Country Status (5)
Country | Link |
---|---|
US (1) | US20170121581A1 (en) |
EP (1) | EP3128259A1 (en) |
JP (1) | JPWO2015140827A1 (en) |
CN (1) | CN106415152A (en) |
WO (1) | WO2015140827A1 (en) |
Cited By (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3598028A4 (en) * | 2017-03-13 | 2020-12-30 | LG Electronics Inc. -1- | Air conditioner |
EP3598030A4 (en) * | 2017-03-13 | 2020-12-30 | LG Electronics Inc. -1- | Air conditioner |
EP3598035A4 (en) * | 2017-03-13 | 2021-01-13 | LG Electronics Inc. | Air conditioner |
EP3598033A4 (en) * | 2017-03-13 | 2021-01-13 | LG Electronics Inc. | Air conditioner |
US11365335B2 (en) | 2017-12-18 | 2022-06-21 | Daikin Industries, Ltd. | Composition comprising refrigerant, use thereof, refrigerating machine having same, and method for operating said refrigerating machine |
US11435118B2 (en) | 2017-12-18 | 2022-09-06 | Daikin Industries, Ltd. | Heat source unit and refrigeration cycle apparatus |
US11441802B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Air conditioning apparatus |
US11441819B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
US11492527B2 (en) | 2017-12-18 | 2022-11-08 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
US11493244B2 (en) | 2017-12-18 | 2022-11-08 | Daikin Industries, Ltd. | Air-conditioning unit |
US11506425B2 (en) | 2017-12-18 | 2022-11-22 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
US11519642B2 (en) | 2017-06-22 | 2022-12-06 | Lg Electronics Inc. | Air conditioner |
US11535781B2 (en) | 2017-12-18 | 2022-12-27 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
US11549041B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
US11549695B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Heat exchange unit |
US11820933B2 (en) | 2017-12-18 | 2023-11-21 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
EP3598027B1 (en) * | 2017-03-13 | 2023-12-20 | LG Electronics Inc. | Air conditioner |
US11906207B2 (en) | 2017-12-18 | 2024-02-20 | Daikin Industries, Ltd. | Refrigeration apparatus |
EP3598034B1 (en) * | 2017-03-13 | 2024-03-06 | LG Electronics Inc. | Air conditioner |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015140994A1 (en) * | 2014-03-20 | 2015-09-24 | 三菱電機株式会社 | Heat source side unit and air conditioner |
JP2017145975A (en) * | 2016-02-15 | 2017-08-24 | 三菱電機株式会社 | Refrigeration cycle device, process of manufacture of refrigeration cycle device, drop-in method for refrigeration cycle device, and replace method for refrigeration cycle device |
JP6721546B2 (en) | 2017-07-21 | 2020-07-15 | ダイキン工業株式会社 | Refrigeration equipment |
KR102364389B1 (en) * | 2017-09-27 | 2022-02-17 | 엘지전자 주식회사 | Air conditioner |
WO2019124146A1 (en) * | 2017-12-18 | 2019-06-27 | ダイキン工業株式会社 | Refrigeration cycle |
US20190203093A1 (en) | 2017-12-29 | 2019-07-04 | Trane International Inc. | Lower gwp refrigerant compositions |
US10655039B2 (en) | 2017-12-29 | 2020-05-19 | Trane International Inc. | Lower GWP refrigerant compositions |
JP2020003086A (en) * | 2018-06-25 | 2020-01-09 | ダイキン工業株式会社 | Refrigeration cycle device |
JP2020003104A (en) * | 2018-06-26 | 2020-01-09 | 株式会社富士通ゼネラル | Air conditioner |
JP2020070941A (en) * | 2018-10-29 | 2020-05-07 | 株式会社富士通ゼネラル | Refrigeration cycle device |
US10752518B2 (en) | 2018-10-30 | 2020-08-25 | Clean Water Ventures, Inc. | Method and apparatus for water purification using continuous hydrothermal oxidation regime |
EP4040085B1 (en) * | 2019-09-30 | 2024-06-05 | Daikin Industries, Ltd. | Refrigeration cycle device |
CN116097048A (en) * | 2020-09-04 | 2023-05-09 | 大金工业株式会社 | Use of refrigerant in refrigeration cycle device and refrigeration cycle device |
JP7445140B2 (en) * | 2021-06-11 | 2024-03-07 | ダイキン工業株式会社 | Air conditioner, installation method of air conditioner, and outdoor unit |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3289366B2 (en) * | 1993-03-08 | 2002-06-04 | ダイキン工業株式会社 | Refrigeration equipment |
JPH10122704A (en) * | 1996-10-23 | 1998-05-15 | Toshiba Corp | Heat exchanger of air conditioner |
EP1698842A3 (en) * | 1999-03-02 | 2009-12-09 | Daikin Industries, Ltd. | Refrigerating apparatus |
DE60032748T2 (en) * | 1999-03-02 | 2007-04-26 | Daikin Industries, Ltd. | COOLING DEVICE |
JP2001248941A (en) * | 1999-12-28 | 2001-09-14 | Daikin Ind Ltd | Refrigeration unit |
CN102177118A (en) * | 2008-10-10 | 2011-09-07 | 纳幕尔杜邦公司 | Compositions comprising 2,3,3,3-tetrafluoropropene, 2-chloro-2,3,3,3-tetrafluoropropanol, 2-chloro-2,3,3,3-tetrafluoro-propyl acetate or zinc (2-chloro-2,3,3,3-tetrafluoropropoxy) chloride |
US20110144216A1 (en) * | 2009-12-16 | 2011-06-16 | Honeywell International Inc. | Compositions and uses of cis-1,1,1,4,4,4-hexafluoro-2-butene |
US8889031B2 (en) * | 2010-11-30 | 2014-11-18 | Jx Nippon Oil & Energy Corporation | Working fluid composition for refrigerator machine and refrigerating machine oil |
DE112012002154B4 (en) * | 2011-05-19 | 2022-06-30 | AGC Inc. | Working medium and its use in a heat cycle process system |
JP5536817B2 (en) * | 2012-03-26 | 2014-07-02 | 日立アプライアンス株式会社 | Refrigeration cycle equipment |
US9459033B2 (en) * | 2012-08-02 | 2016-10-04 | Mitsubishi Electric Corporation | Multi air-conditioning apparatus |
WO2014103028A1 (en) * | 2012-12-28 | 2014-07-03 | 三菱電機株式会社 | Air conditioner |
-
2014
- 2014-03-17 JP JP2016508298A patent/JPWO2015140827A1/en active Pending
- 2014-03-17 CN CN201480077142.6A patent/CN106415152A/en not_active Withdrawn
- 2014-03-17 WO PCT/JP2014/001483 patent/WO2015140827A1/en active Application Filing
- 2014-03-17 EP EP14886307.9A patent/EP3128259A1/en not_active Withdrawn
- 2014-03-17 US US15/125,342 patent/US20170121581A1/en not_active Abandoned
Cited By (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3598030A4 (en) * | 2017-03-13 | 2020-12-30 | LG Electronics Inc. -1- | Air conditioner |
EP3598035A4 (en) * | 2017-03-13 | 2021-01-13 | LG Electronics Inc. | Air conditioner |
EP3598033A4 (en) * | 2017-03-13 | 2021-01-13 | LG Electronics Inc. | Air conditioner |
US11287146B2 (en) | 2017-03-13 | 2022-03-29 | Lg Electronics Inc. | Air conditioner |
EP3598034B1 (en) * | 2017-03-13 | 2024-03-06 | LG Electronics Inc. | Air conditioner |
US11408691B2 (en) | 2017-03-13 | 2022-08-09 | Lg Electronics Inc. | Air conditioner |
US11413713B2 (en) | 2017-03-13 | 2022-08-16 | Lg Electronics Inc. | Air conditioner |
EP3598027B1 (en) * | 2017-03-13 | 2023-12-20 | LG Electronics Inc. | Air conditioner |
US11608539B2 (en) | 2017-03-13 | 2023-03-21 | Lg Electronics Inc. | Air conditioner |
EP3598028A4 (en) * | 2017-03-13 | 2020-12-30 | LG Electronics Inc. -1- | Air conditioner |
US11519642B2 (en) | 2017-06-22 | 2022-12-06 | Lg Electronics Inc. | Air conditioner |
US11441819B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
US11493244B2 (en) | 2017-12-18 | 2022-11-08 | Daikin Industries, Ltd. | Air-conditioning unit |
US11506425B2 (en) | 2017-12-18 | 2022-11-22 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
US11492527B2 (en) | 2017-12-18 | 2022-11-08 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
US11535781B2 (en) | 2017-12-18 | 2022-12-27 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
US11549041B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
US11549695B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Heat exchange unit |
US11441802B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Air conditioning apparatus |
US11820933B2 (en) | 2017-12-18 | 2023-11-21 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
US11435118B2 (en) | 2017-12-18 | 2022-09-06 | Daikin Industries, Ltd. | Heat source unit and refrigeration cycle apparatus |
US11906207B2 (en) | 2017-12-18 | 2024-02-20 | Daikin Industries, Ltd. | Refrigeration apparatus |
US11365335B2 (en) | 2017-12-18 | 2022-06-21 | Daikin Industries, Ltd. | Composition comprising refrigerant, use thereof, refrigerating machine having same, and method for operating said refrigerating machine |
Also Published As
Publication number | Publication date |
---|---|
WO2015140827A1 (en) | 2015-09-24 |
JPWO2015140827A1 (en) | 2017-04-06 |
CN106415152A (en) | 2017-02-15 |
US20170121581A1 (en) | 2017-05-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP3128259A1 (en) | Heat pump device | |
US11535781B2 (en) | Refrigeration cycle apparatus | |
JP6065429B2 (en) | Air conditioner | |
EP2249104A1 (en) | Refrigerating apparatus | |
US20220380648A1 (en) | Refrigeration cycle apparatus | |
CN112673075A (en) | Refrigeration cycle device | |
EP2787297B1 (en) | Method for selecting heat medium of use-side heat exchanger during construction of air conditioning system | |
EP2246649A1 (en) | Refrigerating apparatus | |
EP3287503A1 (en) | Composition for use in heat cycle system, and heat cycle system | |
JP2020502299A (en) | Refrigerants, heat transfer compositions, methods, and systems | |
JP2011094841A (en) | Refrigerating device | |
KR20140116159A (en) | Bubble-removal device, outdoor heat-exchange device, and refrigeration/air-conditioning system | |
JPWO2018193974A1 (en) | Heat cycle system | |
CN113993973B (en) | Refrigerant-containing composition, use thereof, refrigerator having the composition, method for operating the refrigerator, and refrigeration cycle device having the refrigerator | |
EP3575710A1 (en) | Refrigeration device | |
CN107250330A (en) | Refrigerator oil and working fluid composition for refrigerating machine | |
JP6978706B2 (en) | A composition containing a refrigerant, its use, a refrigerator having it, a method of operating the refrigerator, and a refrigerating cycle device having it. | |
EP3121537A1 (en) | Refrigeration cycle apparatus | |
EP2578966A1 (en) | Refrigeration device and cooling and heating device | |
WO2009150763A1 (en) | Air-conditioning device | |
CN112585415A (en) | Air conditioning process | |
JPWO2013084455A1 (en) | Heat exchanger and air conditioner equipped with the same | |
JP4855305B2 (en) | Air conditioner | |
CN107036318A (en) | Refrigerating circulatory device | |
WO2017145243A1 (en) | Refrigeration cycle apparatus |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20161013 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
DAX | Request for extension of the european patent (deleted) | ||
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN |
|
18W | Application withdrawn |
Effective date: 20171018 |